Rotating electric machine system and combined power system equipped therewith

Abstract

To provide a rotary electric machine system in which a rotor is efficiently cooled by lubricating oil.SOLUTION: A rotary electric machine system includes a rotor having a permanent magnet and a rotary shaft 40. The rotary shaft is supported by a rotary electric machine housing via a first bearing 74 and a second bearing 84. A first oil supply passage for supplying the lubricating oil to the first bearing and the second bearing is formed in the rotary electric machine housing. Further, an in-rotor oil passage is formed inside the rotor. A part of the lubricating oil is diverted from the first oil supply passage and supplied to the in-rotor oil passage.SELECTED DRAWING: Figure 12

Description

【Technical Field】 【0001】 The present invention relates to a rotating electrical machine system. The present invention also relates to a hybrid power system in which a rotating electrical machine system and an internal combustion engine are integrally configured. 【Background Art】 【0002】 A rotating electrical machine includes a rotor having a rotating shaft and a stator located on the outer periphery of the rotor. A permanent magnet is held on the rotating shaft. When the rotating shaft rotates, an alternating magnetic field is formed by the permanent magnet and an electromagnetic coil in the stator. As a result, an induced current is generated in the electromagnetic coil. That is, in this case, the rotating electrical machine functions as a generator. 【0003】 When an induced current continuously occurs in the rotating electrical machine, the rotating electrical machine gets hot. Further, when the rotating shaft of a small rotating electrical machine is rotated at a high speed, the fluid (mainly air) between the rotor and the stator becomes a turbulent flow. As a result, the windage loss increases and the frictional resistance between the rotor and the stator increases. Also due to this, the temperatures of the rotor and the stator increase. 【0004】 In any case, the temperature of the permanent magnet becomes high. As the temperature of the permanent magnet approaches the Curie temperature, the magnetic force of the permanent magnet decreases. Along with this, the output of the rotating electrical machine decreases. To avoid this, the rotating electrical machine may be cooled. For example, in Patent Document 1, it is proposed to supply a part of the lubricating oil of an internal combustion engine as cooling oil for cooling the rotating electrical machine. In this case, a holder for holding the permanent magnet is provided on the rotating shaft. The lubricating oil (cooling oil) is sent to an annular cooling oil chamber formed in the holder. 【Prior Art Documents】 【Patent Documents】 【0005】 【Patent Document 1】 Japanese Patent Application Laid-Open No. 2006-230098 【Summary of the Invention】 [Problems that the invention aims to solve] 【0006】 In a rotating electric machine, the rotating shaft is supported by the rotating electric machine housing via bearings. Generally, lubricating oil is supplied to the bearings to prevent seizing. Therefore, in the configuration described in Patent Document 1, it is necessary to supply lubricating oil to the bearings while simultaneously supplying cooling oil to the rotor. In other words, separate oil passages are required for supplying and recovering lubricating oil and for supplying and recovering cooling oil to the rotating electric machine. As a result, the configuration of the rotating electric machine system becomes complex. Furthermore, there is a concern that the rotating electric machine system will become larger as a result. 【0007】 The present invention aims to solve the problems described above. [Means for solving the problem] 【0008】 According to one embodiment of the present invention, a rotating electric machine system is provided, comprising a rotating electric machine having a rotor including a permanent magnet and a rotating shaft, and a rotating electric machine housing that rotatably supports the rotating shaft, wherein the rotating electric machine system comprises a first bearing and a second bearing interposed between the rotating electric machine housing and the rotating shaft, and an oil circulation supply device that circulates and supplies lubricating oil to the first bearing and the second bearing, the rotating electric machine housing having a first oil supply passage that supplies the lubricating oil supplied from the oil circulation supply device to the first bearing and the second bearing, and a second oil supply passage that branches off from the first oil supply passage and supplies the lubricating oil toward the rotor, an internal rotor oil passage formed inside the rotor for circulating the lubricating oil that has flowed out from the second oil supply passage, and the rotating electric machine housing having an oil discharge passage for discharging the lubricating oil that has flowed through the first oil supply passage, the second oil supply passage and the internal rotor oil passage to the oil circulation supply device. 【0009】 According to another embodiment of the present invention, a combined power system is provided comprising the above-described rotating electric machine system and an internal combustion engine, wherein the internal combustion engine has an output shaft that rotates integrally with the rotating shaft of the rotating electric machine system. [Effects of the Invention] 【0010】 In this invention, a portion of the lubricating oil supplied to the bearing is diverted and circulated through the oil passages within the rotor. Based on this circulation, the rotor, which constitutes the rotating electric machine, is efficiently cooled by the lubricating oil. 【0011】 In other words, in this case, a portion of the lubricating oil is used as cooling oil to cool the rotor. Therefore, it is not necessary to provide separate oil passages for supplying and recovering lubricating oil for the bearings and for supplying and recovering cooling oil for the rotor. This eliminates concerns about the complexity of the rotating electric machine's configuration. It also eliminates concerns about the rotating electric machine system becoming larger. 【0012】 Furthermore, since the rotor is cooled by lubricating oil, the temperature of the permanent magnets constituting the rotor is prevented from reaching the Curie temperature. Therefore, the reduction in the magnetic force of the permanent magnets is suppressed. As a result, a predetermined magnetic force is generated in the alternating magnetic field formed between the permanent magnets and the electromagnetic coil. This allows for continuous output from the rotating electric machine. Additionally, the output can be increased by rotating the rotor at high speed. [Brief explanation of the drawing] 【0013】 [Figure 1] Figure 1 is a schematic overall perspective view of a combined power system according to an embodiment of the present invention. [Figure 2] Figure 2 is a schematic overall perspective view of the rotating electric machine system that constitutes the combined power system. [Figure 3] Figure 3 is a schematic side cross-sectional view of a rotating electric machine system. [Figure 4] Figure 4 is an enlarged view of the main part of Figure 3. [Figure 5]FIG. 5 is an enlarged view of the main part of FIG. 3 at a location different from FIG. 4. [Figure 6] FIG. 6 is a cross-sectional side view of the main part showing an outer shaft constituting a rotating shaft and a member provided on the outer shaft. [Figure 7] FIG. 7 is a cross-sectional side view taken along the axial direction in the vicinity of one end (left open end) of the outer shaft. [Figure 8] FIG. 8 is an enlarged view of the main part of FIG. 7. [Figure 9] FIG. 9 is a schematic configuration diagram of a current converter provided in a rotating electrical machine housing. [Figure 10] FIG. 10 is a schematic perspective view of a second sub-housing constituting a rotating electrical machine housing and an inner housing in an engine housing. [Figure 11] FIG. 11 is a schematic cross-sectional side view of a rotating electrical machine system in a phase different from the phase of FIG. 3. [Figure 12] FIG. 12 is a schematic system diagram schematically showing a lubricating oil flow path (second supply path) in a rotating electrical machine system. [Figure 13] FIG. 13 is a schematic cross-sectional side view of a gas turbine engine constituting a compound power system. [Figure 14] FIG. 14 is an enlarged view of the main part of FIG. 13. [Figure 15] FIG. 15 is a schematic cross-sectional side view in the case of using a compression pump provided externally as a gas supply device. 【Embodiments for Carrying Out the Invention】 【0014】 Each of "left", "right", "lower", and "upper" in the following refers to the left, right, lower, and upper directions in FIGS. 3 to 5, FIGS. 13, and FIGS. 14 in particular. However, these directions are for the sake of convenience in simplifying the description and facilitating understanding. That is, the directions described in the specification are not necessarily the directions when the compound power system is actually used. 【0015】 FIG. 1 is a schematic overall perspective view of a hybrid power system 500 according to the present embodiment. The hybrid power system 500 includes a rotating electrical machine system 10 and a gas turbine engine 200. An axis extending along the longitudinal direction (axial direction) through the diameter center of the rotating electrical machine system 10 coincides with an axis extending along the longitudinal direction (axial direction) through the diameter center of the gas turbine engine 200. In other words, the rotating electrical machine system 10 and the gas turbine engine 200 are arranged in parallel on the same axis. 【0016】 Hereinafter, the left end in the axial direction of each of the rotating electrical machine system 10 and the gas turbine engine 200 may be referred to as the first end. Similarly, the right end in the axial direction of each of the rotating electrical machine system 10 and the gas turbine engine 200 may be referred to as the second end. That is, in the rotating electrical machine system 10, the left end portion separated from the gas turbine engine 200 is the first end. In the rotating electrical machine system 10, the right end portion close to the gas turbine engine 200 is the second end. Also, in the gas turbine engine 200, the left end portion close to the rotating electrical machine system 10 is the first end. In the gas turbine engine 200, the right end portion separated from the rotating electrical machine system 10 is the second end. According to this definition, in the illustrated example, the gas turbine engine 200 is disposed at the second end of the rotating electrical machine system 10. The rotating electrical machine system 10 is disposed at the first end of the gas turbine engine 200. 【0017】 The hybrid power system 500 is used as a propulsion power source, for example, in a flying object, a ship, or an automobile. Suitable specific examples of the flying object include a drone or a multicopter. When the hybrid power system 500 is mounted on a flying object, it is used as a power drive source for rotating and urging, for example, a propeller, a ducted fan, or the like. When the hybrid power system 500 is mounted on a ship, it is used as a screw rotational force generating device. When the hybrid power system 500 is mounted on an automobile, it is used as a power drive source for rotating and urging a motor. 【0018】 The combined power system 500 can also be used as a power source for auxiliary power in aircraft, ships, buildings, etc. Furthermore, the combined power system 500 can be used as a gas turbine power generation facility. 【0019】 As will be described later, the gas turbine engine 200 is an internal combustion engine. Furthermore, the gas turbine engine 200 is a gas supply device that provides compressed air (gas). 【0020】 First, let's describe the rotating electric machine system 10. Figure 2 is a schematic overall perspective view of the rotating electric machine system 10. Figure 3 is a schematic side cross-sectional view of the rotating electric machine system 10. This rotating electric machine system 10 comprises a rotating electric machine 12 (for example, a generator) and a rotating electric machine housing 14 that houses the rotating electric machine 12. 【0021】 The rotating electric machine housing 14 comprises a main housing 16, a first sub-housing 18, and a second sub-housing 20. The main housing 16 has a substantially cylindrical shape, with both its first and second ends being open. The first sub-housing 18 is connected to the first end (left open end) of the main housing 16. The second sub-housing 20 is connected to the second end (right open end) of the main housing 16. As a result, the first and second ends of the main housing 16 are closed. 【0022】 The main housing 16 has thick side walls that extend along the left-right direction. The main housing 16 has a hollow interior. This hollow interior is a storage chamber 22. Most of the rotating electric machine 12 is housed in the storage chamber 22. 【0023】 A cooling jacket 24 is formed in a spiral shape inside the side wall of the main housing 16. A cooling medium flows through the cooling jacket 24. A specific example of the cooling medium is cooling water. In this case, the cooling jacket 24 is a water jacket. 【0024】 On the outer surface (outer wall) of the side wall of the main housing 16, a first casing 26 and a second casing 28 are provided near the edge of the first end. The first casing 26 and the second casing 28 are parts of the main housing 16. That is, the first casing 26 and the second casing 28 are provided integrally with the main housing 16. As will be described later, the first casing 26 is a terminal casing. The second casing 28 is a measuring instrument casing. 【0025】 The first casing 26 has a first internal space 29. The second casing 28 has a second internal space (not shown). The first internal space 29 and the second internal space are in communication with each other via a connecting hole (not shown). The first internal space 29 is also in communication with a storage chamber 22. 【0026】 A holding member for holding a rotation parameter detector is connected to the first sub-housing 18. In this embodiment, a resolver 132 is exemplified as the rotation parameter detector. Therefore, the detector holding member will be referred to as the "resolver holder 30" hereafter. As will be described later, a cap cover 32 is connected to the resolver holder 30 via a screw. 【0027】 The rotating electric machine 12 comprises a rotor 34 and a stator 36 that surrounds the outer circumference of the rotor 34. 【0028】 The rotor 34 includes a rotating shaft 40. The rotating shaft 40 has an inner shaft 42 and a hollow cylindrical outer shaft 44. Both ends of the outer shaft 44 are open ends. That is, the outer shaft 44 has a left open end 441 (see Figure 4) and a right open end 442 (see Figure 5). The inner shaft 42 is inserted into the outer shaft 44 so as to be removable. 【0029】 The inner shaft 42 is longer than the outer shaft 44. The inner shaft 42 has a cylindrical section 421, a left end 422 (see Figure 4), and a right end 423 (see Figure 5). The left end 422 is connected to the left of the cylindrical section 421. Therefore, the left end 422 is the end of the inner shaft 42 that is spaced away from the gas turbine engine 200 (the first end). The right end 423 is connected to the right of the cylindrical section 421. Therefore, the right end 423 is the end of the inner shaft 42 that is close to the gas turbine engine 200 (the second end). The diameter of the cylindrical section 421 is smaller than that of the left end 422 and the right end 423. Also, the diameter of the right end 423 is smaller than that of the left end 422. 【0030】 A portion of the left end 422 is exposed from the left opening end 441 of the outer shaft 44. The portion exposed from the left opening end 441 is the protruding tip 46, which will be described later. In the illustrated example, the right end 423 of the inner shaft 42 and the right opening end 442 of the outer shaft 44 are flush. However, the right end 423 may be positioned slightly off-center from the right opening end 442 toward the second end. 【0031】 As shown in detail in Figure 4, the left end 422 of the inner shaft 42 is provided with a first external threaded portion 48, a flange portion 50, a stopper portion 52, and a second external threaded portion 54 in that order from right to left. The outer diameters of the first external threaded portion 48, flange portion 50, stopper portion 52, and second external threaded portion 54 increase in this order. The outer diameter of the second external threaded portion 54 is larger than the inner diameter of the outer shaft 44. Therefore, the right end of the second external threaded portion 54 abuts against the edge of the left open end 441 of the outer shaft 44. Consequently, the portion of the inner shaft 42 to the left of the second external threaded portion 54 is not inserted into the outer shaft 44. 【0032】 A resolver rotor 56 is mounted on the flange portion 50. A small cap nut 58 is screwed onto the first external thread portion 48. The right end of the resolver rotor 56 is positioned by the stopper portion 52. The left end of the resolver rotor 56 is pressed by the small cap nut 58. In this way, the resolver rotor 56 is positioned and fixed to the flange portion 50. 【0033】 Furthermore, a large cap nut 60 is screwed onto the second external thread portion 54. The right end of the large cap nut 60 covers the outer peripheral wall of the left open end 441 of the outer shaft 44. As a result, the left end portion 422 of the inner shaft 42 is restrained by the left open end 441 of the outer shaft 44. Note that both the first external thread portion 48 and the second external thread portion 54 are so-called reverse threads. Therefore, the small cap nut 58 and the large cap nut 60 are rotated counterclockwise when screwed on. After screwing, it is preferable to deform a portion of the threads of the small cap nut 58 and the large cap nut 60. This prevents the small cap nut 58 and the large cap nut 60 from loosening. 【0034】 As shown in Figure 5, a connecting hole 62 is formed in the right end 423, which is the second end of the inner shaft 42. The connecting hole 62 extends toward the left end 422, which is the first end. A female threaded portion 64 is engraved on the inner circumferential wall of the connecting hole 62. The left end of the output shaft 204 is inserted into the connecting hole 62. The left end of the output shaft 204 is connected to the inner shaft 42 by screwing it into the female threaded portion 64. The output shaft 204 holds the compressor wheel 222 and the turbine wheel 224 (see Figure 13). 【0035】 Furthermore, a first internal spline 66 is formed on the outer peripheral wall of the right open end 442 of the outer shaft 44. The first internal spline 66 extends along the axial direction (left-right direction) of the rotating electric machine system 10. 【0036】 As shown in detail in Figure 6, the outer shaft 44 has first shaft sections 44a to sixth shaft sections 44f in this order from the first end to the second end. The outer diameters (diameters) of the first shaft sections 44a to sixth shaft sections 44f differ from each other. Specifically, the outer diameter increases from the first shaft section 44a to the fifth shaft section 44e. That is, for example, the second shaft section 44b is larger in diameter than the first shaft section 44a and smaller in diameter than the third shaft section 44c. Similarly, the third shaft section 44c is larger in diameter than the second shaft section 44b and smaller in diameter than the fourth shaft section 44d. Thus, the outer shaft 44 changes from a small diameter section to a large diameter section from the first shaft section 44a to the fifth shaft section 44e. In contrast, the outer diameter of the sixth shaft section 44f is smaller than the outer diameters of the third shaft section 44c to the fifth shaft section 44e. 【0037】 A first stage 330 is formed between the first shaft portion 44a and the second shaft portion 44b based on the difference in outer diameter (diameter difference) between the two shaft portions 44a and 44b. A second stage 332 is formed between the second shaft portion 44b and the third shaft portion 44c based on the difference in outer diameter between the two shaft portions 44b and 44c. A third stage 334 is formed between the third shaft portion 44c and the fourth shaft portion 44d based on the difference in outer diameter between the two shaft portions 44c and 44d. A fourth stage 336 is formed between the fourth shaft portion 44d and the fifth shaft portion 44e based on the difference in outer diameter between the two shaft portions 44d and 44e. 【0038】 As will be described later, the first stage 330, the second stage 332, the third stage 334, and the fourth stage 336 are direction-changing sections that change the direction of lubrication oil flow. In this embodiment, the first stage 330, the second stage 332, the third stage 334, and the fourth stage 336 are shown as vertical surfaces. However, at least one of the first stage 330, the second stage 332, the third stage 334, or the fourth stage 336 may be an inclined surface. 【0039】 Figure 7 is a side cross-sectional view of the vicinity of the left open end 441 of the outer shaft 44, viewed along the axial direction. Figure 8 is an enlarged view of the main part of Figure 7. As shown in Figures 7 and 8, an oil receiving recess 340 is formed near the first end of the first shaft portion 44a. The oil receiving recess 340 is an annular recess formed on the outer surface of the first shaft portion 44a. 【0040】 The side wall facing the first end of the oil receiving recess 340 is an inclined surface 342 that slopes so as it approaches the inner shaft 42 from the first end to the second end. The inclination angle of the inclined surface 342 is approximately equal to the inclination angle of the outlet of the second auxiliary oil passage 181. The bottom surface 346 of the oil receiving recess 340 is connected to the inclined surface 342. The bottom surface 346 is formed in the outer shaft 44 at a point where the outer diameter is constant. 【0041】 In the first shaft portion 44a, an annular first threaded portion 348 is formed on the second end side of the oil receiving recess 340. The second threaded portion 352 of the oil guide member 350 is screwed into the first threaded portion 348. 【0042】 The rotating shaft 40 has an oil guide member 350 which is an annular shape. Specifically, the oil guide member 350 is positioned and fixed to the outer circumferential wall of the first shaft portion 44a. That is, as described above, the first shaft portion 44a has a first threaded portion 348, and the oil guide member 350 has a second threaded portion 352 (see Figures 7 and 8). The oil guide member 350 is positioned and fixed to the first shaft portion 44a by screwing (engaging) the second threaded portion 352 into the first threaded portion 348. 【0043】 As shown in Figures 7 and 8, an annular projection 380 is provided on the first end edge of the oil guide member 350. The annular projection 380 protrudes inward in the diametrical direction of the oil guide member 350. In addition, an annular protrusion 382 is provided on the inner circumferential wall of the oil guide member 350. The annular protrusion 382 protrudes inward in the diametrical direction of the oil guide member 350 at a position closer to the second end than the annular projection 380. The amount of protrusion of the annular protrusion 382 is greater than the amount of protrusion of the annular projection 380. 【0044】 The annular projection 380 and the annular protrusion 382 form an annular groove 384 inside the first end of the oil guide member 350. The annular groove 384 faces the bottom surface 346 of the oil receiving recess 340. In this way, the oil guide member 350 is positioned to face the oil receiving recess 340 formed in the rotating shaft 40 (the first shaft portion 44a of the outer shaft 44). An annular gap 385 is formed between the oil guide member 350 and the rotating shaft 40 to receive lubricating oil into the oil guide member 350. Specifically, the annular gap 385 is formed between the oil receiving recess 340 and the annular projection 380. 【0045】 As will be described later, the annular gap 385 is the inlet of the rotor internal oil passage 354. The outlet of the rotor internal oil passage 354 is an opening facing the second end of the hole in the second magnet stopper 358. Thus, the inlet of the rotor internal oil passage 354 is outside the first bearing 74 in the axial direction of the rotating shaft 40. On the other hand, the outlet of the rotor internal oil passage 354 is inside the second bearing 84 in the axial direction of the rotating shaft 40. 【0046】 As shown in Figure 8, multiple first oil supply passages 386 are formed in the annular protrusion 382. The first oil supply passages 386 extend along the axial direction of the rotating shaft 40 (see Figure 7). The outlets of the multiple first oil supply passages 386 lead to an annular space 388. The annular space 388 is a space formed inside the second end of the oil guide member 350. The annular space 388 communicates with the flow space 374, which is part of the rotor internal oil passage 354. In other words, the first oil supply passages 386 communicate with the rotor internal oil passage 354 via the annular space 388. 【0047】 The second threaded portion 352 is a projection that protrudes further diametrically inward from the annular projection 382. The length of the annular projection 382 along the axial direction of the rotating shaft 40 is slightly greater than the length of the second threaded portion 352 along the axial direction of the rotating shaft 40. 【0048】 Multiple upstream guide grooves 390 (first guide grooves) are formed on the outer circumferential wall of the oil guide member 350. Two adjacent upstream guide grooves 390 are spaced, for example, 60° apart. 【0049】 A first outer stopper 81, which is one of the bearing stoppers, is provided at the second end of the first shaft portion 44a. A first inner stopper 82, which is one of the bearing stoppers, is provided at the second shaft portion 44b. A first bearing 74 is sandwiched between the first outer stopper 81 and the first inner stopper 82. The above will be described later. 【0050】 As shown in Figure 6, permanent magnets 72 are held in the third shaft portion 44c to the fifth shaft portion 44e via a cylindrical member 70. The rotor 34 is composed of a rotating shaft 40, a cylindrical member 70, and permanent magnets 72. An inner hole 73 is formed in the cylindrical member 70, extending along the axial direction of the cylindrical member 70. The rotating shaft 40 passes through the inner hole 73. Therefore, the cylindrical member 70 is interposed between the rotating shaft 40 and the permanent magnets 72 in the diametrical direction of the rotating shaft 40. In the inner hole 73, the inner diameter is larger in the portion corresponding to the third stage portion 334. 【0051】 As the rotating shaft 40 rotates, the permanent magnet 72 moves along the circumference of a predetermined virtual circle with respect to the rotation center of the rotating shaft 40. 【0052】 The cylindrical member 70 and the permanent magnet 72 are sandwiched between the first magnet stopper 356 and the second magnet stopper 358 in the axial direction of the rotating shaft 40. This positions the cylindrical member 70 within the third shaft portion 44c to the fifth shaft portion 44e. In other words, misalignment of the cylindrical member 70 and the permanent magnet 72 from the third shaft portion 44c to the fifth shaft portion 44e is prevented. In this way, the first magnet stopper 356 and the second magnet stopper 358 position the permanent magnet 72. 【0053】 The first magnet stopper 356 straddles the second end of the second shaft portion 44b and the first end of the third shaft portion 44c. The second magnet stopper 358 covers the outer surface of the fifth shaft portion 44e. A first ring body 363 is sandwiched between the first magnet stopper 356 and the permanent magnet 72. Similarly, a second ring body 364 is sandwiched between the permanent magnet 72 and the second magnet stopper 358. The first and second ends of the cylindrical member 70 are passed through the through holes of the first ring body 363 and the second ring body 364, respectively. 【0054】 An inward projection 3581 is provided on the inner circumferential wall of the hole in the second magnet stopper 358. The inward projection 3581 protrudes in an annular shape toward the diametrically inward direction of the hole. The inner circumferential wall of the inward projection 3581 abuts against the top surface of the fourth stage 336. Multiple second oil supply passages 3582 are formed in the inward projection 3581. The multiple second oil supply passages 3582 are arranged along the circumferential direction of the inward projection 3581. One of the second oil supply passages 3582 extends along the axial direction of the rotating shaft 40. 【0055】 As shown in Figure 3, the left end (first end) of the rotating shaft 40 is rotatably supported by the first sub-housing 18 via a first bearing 74. The first bearing 74 is inserted between the outer shaft 44 and the first sub-housing 18. Specifically, the first sub-housing 18 has a cylindrical projection 76 that protrudes toward the main housing 16, as shown in Figures 3 and 7. A first insertion hole 78 is formed in the cylindrical projection 76. A first bearing holder 80, which holds the first bearing 74, is inserted into the first insertion hole 78. Thus, the first bearing 74 is positioned in the first insertion hole 78. 【0056】 The first insertion hole 78 extends along the left-right direction. The left end of the first insertion hole 78 is further away from the output shaft 204 than the right end of the first insertion hole 78. Hereinafter, the left end of the first insertion hole 78 will also be referred to as the "first distal end 781". On the other hand, the right end of the first insertion hole 78 is closer to the output shaft 204 than the left end of the first insertion hole 78 (first distal end 781). Hereinafter, the right end of the first insertion hole 78 will also be referred to as the "first proximal end 782". 【0057】 In particular, as shown in Figure 7, a first outer stopper 81 is provided at the first end of the first shaft portion 44a. The first outer stopper 81 is an annular shape, and a plurality of downstream guide grooves 368 (second guide grooves) are formed on its outer circumferential wall. Two adjacent downstream guide grooves 368 are spaced, for example, 60° apart. It is preferable that the phases of the upstream guide groove 390 and the downstream guide grooves 368 coincide, but it is not necessary for them to coincide. 【0058】 A first inner stopper 82 is provided on the second shaft portion 44b. The first inner stopper 82 has a small diameter cylindrical portion 370 with a small outer diameter and a large diameter cylindrical portion 372 with a large outer diameter. The inner diameters of the small diameter cylindrical portion 370 and the large diameter cylindrical portion 372 are approximately the same. As can be understood from this, the first inner stopper 82 is cylindrical in shape with a hole. The first inner stopper 82 covers the outer surface of the second shaft portion 44b such that the small diameter cylindrical portion 370 faces the first end and the large diameter cylindrical portion 372 faces the second end. 【0059】 As described above, an annular flow space 374 is formed between the first shaft portion 44a and the second shaft portion 44b and the inner circumferential wall of the first inner stopper 82. An annular flow space 360 ​​is also formed between the outer surfaces of the second shaft portion 44b and the third shaft portion 44c and the inner circumferential wall of the hole in the first magnet stopper 356. An annular flow space 353 is also formed between the outer surfaces of the third shaft portion 44c to the fifth shaft portion 44e and the inner wall of the inner hole 73 of the cylindrical member 70. An annular flow space 362 is also formed between the outer surface of the sixth shaft portion 44f and the inner circumferential wall of the hole in the second magnet stopper 358. The flow spaces 374, 360, 353, and 362 are connected to form the rotor internal oil passage 354. The flow space 353 and the flow space 362 are connected via the second oil supply passage 3582. 【0060】 The rotor oil passage 354 is a flow path extending along the axial direction of the rotating shaft 40, and may be, for example, a partially annular space in the axial direction. The rotor oil passage 354 extends from the first end to the second end of the permanent magnet 72 in the axial direction of the rotating shaft 40. The rotor oil passage 354 may be a groove or the like. 【0061】 The end face of the second end of the oil guide member 350 abuts against the end face of the first end of the small diameter cylindrical portion 370. The end face of the first end of the first magnet stopper 356 abuts against the end face of the second end of the large diameter cylindrical portion 372. In addition, the first outer stopper 81 is positioned and fixed to the outer peripheral wall of the first end of the small diameter cylindrical portion 370. The first bearing 74 is arranged on the outer circumference of the small diameter cylindrical portion 370 and is sandwiched between the end face of the second end of the first outer stopper 81 and the end face of the first end of the large diameter cylindrical portion 372. 【0062】 The tip of the left end of the rotating shaft 40 passes through the inner bore of the first bearing 74 and then through the first insertion hole 78. The tip of the left end of the rotating shaft 40 is further exposed to the outside of the cylindrical projection 76 (hollow recess 118). Hereinafter, the portion of the rotating shaft 40 that protrudes from the left end of the first bearing 74 will be referred to as the "protruding tip 46". The protruding tip 46 includes the first external thread portion 48, the flange portion 50, the stopper portion 52, and the second external thread portion 54 of the left end 422 of the inner shaft 42 (see Figure 4). 【0063】 A second bearing 84 is provided on the sixth shaft portion 44f of the outer shaft 44. The second bearing 84 rotatably supports the right end (second end) of the rotating shaft 40 in the second sub-housing 20. As shown in Figure 5, the second bearing 84 is inserted between the outer shaft 44 and the second sub-housing 20, which has a roughly disc shape. 【0064】 The second sub-housing 20 is connected to the main housing 16 via bolts (not shown). The center of the second sub-housing 20 is a thick-walled cylindrical portion. A second insertion hole 86 is formed in this cylindrical portion. The second insertion hole 86 extends along the left-right direction. The left end of the second insertion hole 86 is further away from the output shaft 204 than the right end of the second insertion hole 86. Hereinafter, the left end of the second insertion hole 86 will also be referred to as the "second distal end 861". On the other hand, the right end of the second insertion hole 86 is closer to the output shaft 204 than the left end (second distal end 861). Hereinafter, the right end of the second insertion hole 86 will also be referred to as the "second proximal end 862". 【0065】 A second bearing holder 88, which holds the second bearing 84, is inserted into the second insertion hole 86. Thus, the second bearing 84 is positioned in the second insertion hole 86. The second bearing 84 is held between a second inner stopper 90 located at the second distal end 861 and a second outer stopper 92 located at the second proximal end 862. Based on this holding, the second bearing 84 is positioned and fixed to the sixth shaft portion 44f. In this way, the second inner stopper 90 and the second outer stopper 92 are bearing stoppers. 【0066】 The rotor 34 has a disc portion 392 as shown in Figures 3 and 6. The disc portion 392 is provided at the first end of the second internal stopper 90 and is a projection that protrudes radially outward from the rotating shaft 40 on the outer circumference of the rotating shaft 40. The disc portion 392 is located between the permanent magnet 72 and the second bearing 84 and partially covers the opening 358a of the hole in the second magnet stopper 358. In this case, the disc portion 392 is a shielding portion provided at the outlet of the flow space 362 (outlet of the rotor internal oil passage 354). The disc portion 392 faces the second bearing 84 in the axial direction of the rotating shaft 40. Because the disc portion 392 partially shields the outlet of the flow space 362, the lubricating oil that has come into contact with the second bearing 84 is separated from the lubricating oil that has flowed out from the rotor internal oil passage 354. The disc portion 392 is located closer to the inside (first end) than the second bearing 84. 【0067】 Furthermore, at the second distal end 861, a clearance is formed between the second internal stopper 90 and the second bearing holder 88. This clearance is the third sub-branch 941. 【0068】 As shown in Figures 2 and 3, a flow straightening member 96 is connected to the end face of the second sub-housing 20 facing the gas turbine engine 200. The flow straightening member 96 has a base portion 98, a reduced diameter portion 100, and a top portion 102. The base portion 98 facing the second sub-housing 20 is a large-diameter, thin-walled cylindrical plate. The top portion 102 facing the gas turbine engine 200 is a small-diameter, relatively long cylindrical plate. In the reduced diameter portion 100 between the base portion 98 and the top portion 102, the diameter gradually decreases. Therefore, the flow straightening member 96 is a V-shaped or bottomless cup-shaped body. The outer surface of the reduced diameter portion 100 is a smooth surface with low surface roughness. 【0069】 At the base portion 98, an inlet 104 is formed on the end face facing the second sub-housing 20. The reduced diameter portion 100 is hollow; that is, a relay chamber 106 is formed inside the reduced diameter portion 100. The inlet 104 is the input port for compressed air to the relay chamber 106. 【0070】 An insertion hole 108 is formed in the top portion 102, extending in the left-right direction. The diameter (opening diameter) of the insertion hole 108 is larger than the outer diameter of the portion of the second outer stopper 92 that extends along the rotating shaft 40. Therefore, the portion of the second outer stopper 92 that enters the insertion hole 108 and its outer peripheral wall are spaced apart from the inner wall of the insertion hole 108. In other words, a clearance is formed between the outer peripheral wall of the second outer stopper 92 and the inner wall of the insertion hole 108. This clearance is the fourth sub-branch 942. The relay chamber 106 widens as it approaches the insertion hole 108 and the fourth sub-branch 942. 【0071】 Furthermore, the diameter (opening diameter) of the through hole 108 is larger than the outer diameter of the relatively small left end (small diameter cylindrical portion 242) of the compressor wheel 222. Therefore, the small diameter cylindrical portion 242 that enters the through hole 108 is also spaced apart from the inner wall of the through hole 108. In other words, a clearance is formed between the outer circumferential wall of the small diameter cylindrical portion 242 and the inner wall of the through hole 108. This clearance is the outlet passage 943. 【0072】 As shown in Figure 3, the first insertion hole 78 and the third sub-branch 941 communicate with the storage chamber 22. Therefore, the first bearing 74 and the second bearing 84 are exposed to the storage chamber 22. 【0073】 The stator 36, together with the rotor 34 described above, constitutes the rotating electric machine 12. The stator 36 has an electromagnetic coil 110 and a plurality of insulating base materials 112. The electromagnetic coil 110 has three types: U-phase coil, V-phase coil, and W-phase coil, and is wound around the insulating base materials 112. If the rotating electric machine 12 is a generator, the rotating electric machine 12 is a so-called three-phase power supply. The plurality of insulating base materials 112 are arranged in a ring shape. This arrangement creates an internal hole in the stator 36. 【0074】 The stator 36 is housed in the storage chamber 22. Here, the second sub-housing 20 serves as the stator holder. Specifically, an annular recess 114 is formed in the second sub-housing 20. The insulating base material 112 included in the stator 36 engages with the annular recess 114. This engagement positions and fixes the stator 36. Furthermore, a cylindrical projection 76 enters the left opening of the inner bore of the stator 36. 【0075】 The inner wall of the storage chamber 22 and the electromagnetic coil 110 are slightly separated from each other. This separation electrically insulates the main housing 16 from the electromagnetic coil 110. 【0076】 A clearance is formed between the outer circumferential wall of the cylindrical projection 76 and the insulating substrate 112. A clearance is also formed between the outer wall of the permanent magnet 72 and the inner wall of the electromagnetic coil 110. As will be described later, compressed air, which is a gas, flows through these clearances. In other words, these clearances are part of the compressed air passage. 【0077】 As shown in Figure 4, the first sub-housing 18 has an annular projection 116 that protrudes in a ring shape. The inside of the annular projection 116 is a hollow recess 118. The protruding tip 46, which is part of the left end 422 of the inner shaft 42, enters the hollow recess 118. 【0078】 A resolver holder 30 is provided on the annular projection 116. The resolver holder 30 has a flange-shaped stopper 120 that protrudes diametrically outward. The flange-shaped stopper 120 has a larger diameter than the inner diameter of the annular projection 116. Therefore, the flange-shaped stopper 120 abuts against the annular projection 116. This abutment positions the resolver holder 30. In this state, the resolver holder 30 is connected to the first sub-housing 18, for example, via mounting bolts (not shown). 【0079】 In the resolver holder 30, a small cylindrical portion 122 is provided to the left of the flange-shaped stopper 120. A large cylindrical portion 124 is provided to the right of the flange-shaped stopper 120. The large cylindrical portion 124 has a larger diameter than the small cylindrical portion 122. A retaining hole 126 is formed in the resolver holder 30. Most of the resolver stator 130 is fitted into the retaining hole 126. This fitting holds the resolver stator 130 in the resolver holder 30. 【0080】 When the large cylindrical portion 124 enters the hollow recess 118 and the flange-shaped stopper 120 contacts the annular protrusion 116, the resolver rotor 56 is positioned in the inner bore of the resolver stator 130. The resolver stator 130 and the resolver rotor 56 constitute the resolver 132. The resolver 132 is a rotation parameter detector. In this embodiment, the resolver 132 detects the rotation angle of the inner shaft 42. As described above, the resolver rotor 56 is held by the flange portion 50 of the left end portion 422 of the inner shaft 42. 【0081】 An engagement hole 134 is formed in the flange-shaped stopper 120. The transmitting connector 136 is engaged with the engagement hole 134. The resolver stator 130 and the transmitting connector 136 are electrically connected via a signal line 138. The receiving connector of a receiver (not shown) is inserted into the transmitting connector 136. The resolver 132 and the receiver are electrically connected via the transmitting connector 136 and the receiving connector. The receiver receives the signal emitted by the resolver 132. 【0082】 Multiple tab portions 140 are provided on the small cylindrical portion 122 (omitted in Figure 1). Figure 3 shows one tab portion 140. Furthermore, a cap cover 32 is placed over the small cylindrical portion 122. The cap cover 32 closes the left opening of the small cylindrical portion 122 and shields the left end portion 422 of the inner shaft 42. The cap cover 32 is connected to the tab portions 140 via connecting bolts 142. 【0083】 As described above, a first casing 26 and a second casing 28 are integrally provided on the side wall near the left end of the main housing 16. The first casing 26 houses a U-phase terminal 1441, a V-phase terminal 1442, and a W-phase terminal 1443. The U-phase terminal 1441 is electrically connected to the U-phase coil of the electromagnetic coil 110. The V-phase terminal 1442 is electrically connected to the V-phase coil of the electromagnetic coil 110. The W-phase terminal 1443 is electrically connected to the W-phase coil of the electromagnetic coil 110. The U-phase terminal 1441, V-phase terminal 1442, and W-phase terminal 1443 are electrical terminals to which external equipment (external load or external power supply) is electrically connected. The power generated by the rotating electric machine 12 is supplied to the external equipment. An example of an external load is a motor (not shown). Another example of external equipment is the battery 146 shown in Figure 9. 【0084】 The second casing 28 is adjacent to the first casing 26. The second casing 28 houses a thermistor 148, which is a temperature measuring instrument. Although not specifically shown in the diagram, the measuring terminals of the thermistor 148 are led out from the second casing 28 and connected to the electromagnetic coil 110. A harness 149 connected to the thermistor 148 is led out from the second casing 28 to the outside. 【0085】 As shown in Figures 1 and 2, a current converter 150 is provided on the outer periphery wall of the main housing 16. The current converter 150 is positioned closer to the gas turbine engine 200 than the first casing 26. As shown in Figure 9, the current converter 150 includes a conversion circuit 152, a capacitor 154, and a control circuit 156. These conversion circuit 152, capacitor 154, and control circuit 156 are housed in an equipment case 158. The equipment case 158 is positioned, for example, on the outer periphery wall of the main housing 16 in a location that does not interfere with the first hollow tube section 1601, the second hollow tube section 1602, and the third hollow tube section 1603 (see Figure 1). 【0086】 The hollow interiors of the first hollow tube section 1601, the second hollow tube section 1602, and the third hollow tube section 1603 are compressed air passages through which compressed air flows. In other words, in this embodiment, three compressed air passages are formed in the rotating electric machine housing 14. The first hollow tube section 1601 and the third hollow tube section 1603 are formed as hollow bulges that protrude from the outer peripheral wall of the main housing 16. 【0087】 The conversion circuit 152 includes a power module 161. The conversion circuit 152 converts the alternating current generated in the electromagnetic coil 110 into a direct current. At this time, the capacitor 154 temporarily stores the direct current converted by the conversion circuit 152 as an electric charge. The conversion circuit 152 also has the function of converting the direct current supplied from the battery 146 into an alternating current. In this case, the capacitor 154 temporarily stores the direct current supplied from the battery 146 to the electromagnetic coil 110 as an electric charge. 【0088】 The control circuit 156 controls the current density of the DC current flowing from the capacitor 154 to the battery 146, or in the reverse direction. The DC current from the battery 146 is supplied to a motor (not shown) via, for example, an AC-to-DC converter. 【0089】 The rotating electric machine system 10, configured as described above, is provided with a compressed air passage and a lubricating oil passage (a first oil supply passage and a second oil supply passage). First, the compressed air passage will be described. 【0090】 As shown in Figure 10, in the second sub-housing 20, an annular manifold passage 162 consisting of an annular recess is formed on the end face facing the gas turbine engine 200. As will be described later, a portion of the compressed air generated by the gas turbine engine 200 flows through the manifold passage 162. Three upstream communication holes 164 are formed in the bottom wall of the manifold passage 162 (annular recess). The upstream communication holes 164 are input ports for compressed air. 【0091】 An air relay path 166 is provided inside the second sub-housing 20. The air relay path 166 extends radially along the diametrical direction of the second sub-housing 20. The air relay path 166 communicates with the manifold flow path 162 via an upstream communication hole 164 in the diametrically outward direction. In addition, three first downstream communication holes 1681 to 1683 are formed on the end face of the second sub-housing 20 facing the rotating electric machine 12. The first downstream communication holes 1681 to 1683 are the first output ports of the air relay path 166. A distribution path is formed by the manifold flow path 162 and the air relay path 166. 【0092】 In the second sub-housing 20, three second downstream communication holes 1701 to 1703 are formed on the end face facing the gas turbine engine 200. The second downstream communication holes 1701 to 1703 are the second output ports of the air relay path 166. The second downstream communication holes 1701 to 1703 are located diametrically inward from the first downstream communication holes 1681 to 1683. Therefore, the compressed air flowing through the air relay path 166 is divided into compressed air entering the first downstream communication holes 1681 to 1683 and compressed air entering the second downstream communication holes 1701 to 1703. 【0093】 As shown in Figure 2, the outer surface of the side wall of the main housing 16 is provided with a first hollow tube section 1601, a second hollow tube section 1602, and a third hollow tube section 1603. The first downstream communication holes 1681 to 1683 each open individually toward the first hollow tube section 1601 to the third hollow tube section 1603. As can be seen from this, the air relay path 166 connects the collective flow path 162 with the hollow interiors of the first hollow tube section 1601 to the third hollow tube section 1603. As shown in Figure 3, the first hollow tube section 1601 to the third hollow tube section 1603 are located diametrically outward from the cooling jacket 24 formed inside the side wall of the main housing 16. 【0094】 The first to third hollow tube sections 1601 to 1603 extend along the axial direction of the main housing 16. That is, the first to third hollow tube sections 1601 to 1603 extend from the second end facing the gas turbine engine 200 toward the first casing 26 (or first end). The hollow interior of the first hollow tube section 1601 communicates with the second internal space of the second casing 28. The hollow interiors of the second and third hollow tube sections 1602 and 1603 communicate with the first internal space 29 of the first casing 26. 【0095】 As will be described later, the compressed air that flows through the hollow interior of the first hollow tube section 1601 forms an air curtain in the second internal space of the second casing 28. Subsequently, the compressed air flows into the first internal space 29 of the first casing 26. The curtain air that flows through the hollow interiors of the second hollow tube section 1602 and the third hollow tube section 1603 flows into the first internal space 29 of the first casing 26. As can be understood from this, the hollow interiors of the first to third hollow tube sections 1601 to 1603 are gas supply passages for supplying compressed air. Furthermore, in the direction of compressed air flow, the first casing 26 and the second casing 28 are downstream of the first to third hollow tube sections 1601 to 1603. 【0096】 As described above, the first internal space 29 of the first casing 26 and the second internal space of the second casing 28 are in communication with each other via a connecting hole. Furthermore, the first internal space 29 of the first casing 26 is in communication with the storage chamber 22. Therefore, compressed air that has flowed through the first hollow pipe section 1601 to the third hollow pipe section 1603 flows into the storage chamber 22 via the first internal space 29 of the first casing 26. 【0097】 In this embodiment, the case in which the first hollow tube section 1601 to the third hollow tube section 1603 are provided is illustrated, but the number of hollow tube sections is appropriately determined according to the flow rate or velocity required for the curtain air formed from compressed air. In other words, the number of hollow tube sections is not limited to three. Similarly, the cross-sectional area of ​​the hollow tube sections is also appropriately determined according to the flow rate or velocity required for the curtain air. 【0098】 The compressed air that flows into the storage chamber 22 then splits into compressed air that goes towards the first insertion hole 78 and compressed air that goes towards the second insertion hole 86. Specifically, a portion of the compressed air flows through the clearance between the first sub-housing 18 and the rotor 34 and goes towards the first insertion hole 78. Thus, the clearance between the first sub-housing 18 and the rotor 34 is the first air branching path L. On the other hand, the remaining portion of the compressed air mainly flows through the clearance between the outer wall of the permanent magnet 72 and the inner wall of the electromagnetic coil 110 and goes towards the second insertion hole 86. Thus, the clearance between the outer wall of the permanent magnet 72 and the inner wall of the electromagnetic coil 110 is the second air branching path M. 【0099】 The compressed air reaching the first air branch L forms an air curtain that seals the lubricating oil supplied to the first bearing 74. Similarly, the compressed air reaching the third sub-branch 941 (the second distal end 861 of the second insertion hole 86) from the second air branch M also forms an air curtain that seals the lubricating oil supplied to the second bearing 84. Thus, the compressed air flowing into the storage chamber 22 functions as a curtain air. 【0100】 As shown in Figure 5, three inlets 104 are formed in the base portion 98 of the rectifier member 96. One of them is shown in Figure 5. One inlet 104 is connected to the second downstream communication hole 1701 (not shown). Another inlet 104 is connected to the second downstream communication hole 1702 (shown). Yet another inlet 104 is connected to the second downstream communication hole 1703 (not shown). Therefore, compressed air output from the second downstream communication holes 1701 to 1703 enters the relay chamber 106 of the reduced diameter portion 100 of the rectifier member 96 via the inlets 104. 【0101】 The relay chamber 106 is connected to the through hole 108 formed in the top portion 102. Here, the relay chamber 106 widens as it approaches the through hole 108 and the fourth sub-branch 942. As a result, the pressure of the curtain air decreases as the compressed air flows through the relay chamber 106. 【0102】 The outlet of the relay chamber 106 faces the small-diameter cylindrical portion 242 of the compressor wheel 222. Therefore, the compressed air entering the relay chamber 106 comes into contact with the small-diameter cylindrical portion 242 of the compressor wheel 222. The compressed air then splits into compressed air heading toward the fourth sub-branch 942 and compressed air heading toward the outlet 943. As a result, the pressure of the compressed air heading toward the second proximal end 862 of the second insertion hole 86 along the fourth sub-branch 942 decreases. 【0103】 The compressed air that reaches the second proximal end 862 of the second insertion hole 86 from the fourth sub-branch passage 942 forms an air curtain that seals the lubricating oil supplied to the second bearing 84. The compressed air that flows into the outlet passage 943 is led inward to the first end (open end) of the shroud case 220. This compressed air is then drawn back into the compressor wheel 222. 【0104】 An exhaust passage 172 (gas discharge passage) is formed in the main housing 16. Compressed air that reaches the first air branch passage L and compressed air that reaches the second air branch passage M are exhausted to the outside of the main housing 16 via the exhaust passage 172. 【0105】 Next, the lubrication oil flow path will be described. Figure 11 is a schematic side cross-sectional view of the rotating electric machine system 10. Note that Figure 11 shows a different phase than that shown in Figure 3. 【0106】 An input passage 174 for supplying lubricating oil is formed in the side wall of the main housing 16. The input passage 174 is formed at a position closer to the first end than the axial midpoint of the main housing 16. The input passage 174 extends along the diametrical direction of the main housing 16 and communicates with the main oil passage 176. The main oil passage 176 is formed on the outer circumference of the cooling jacket 24 and extends along the axial direction of the main housing 16. The main oil passage 176 branches at the point of communication with the input passage 174 into a first oil branch passage N leading to the first sub-housing 18 and a second oil branch passage R leading to the second sub-housing 20. 【0107】 In the first sub-housing 18, a first inlet hole 178 is formed at the location facing the first oil branch passage N. Furthermore, a first secondary oil passage 180 (first oil supply passage) is formed inside the first sub-housing 18, extending diametrically inward. The first secondary oil passage 180 bends at two points before reaching the first bearing holder 80. 【0108】 A second secondary oil passage 181 (second oil supply passage) branches off from the first secondary oil passage 180. Here, as shown in Figures 7, 8, and 11, the first sub-housing 18 has a protruding end 400 that projects toward the oil guide member 350. The tip of the second secondary oil passage 181 extends into the interior of the protruding end 400. The outlet of the second secondary oil passage 181 is slightly bent. The outlet of the second secondary oil passage 181 is a nozzle 181a that discharges lubricating oil toward the annular gap 385 of the rotor 34. In this way, the second secondary oil passage 181 supplies lubricating oil toward the annular gap 385. 【0109】 The first bearing holder 80 has a first oil supply hole 182 that communicates with the first secondary oil passage 180. The outlet of the first oil supply hole 182 is formed at the first distal end 781 of the first insertion hole 78. Therefore, the lubricating oil that flows from the main oil passage 176 into the first secondary oil passage 180 flows from the first oil supply hole 182 to the first distal end 781 of the first insertion hole 78 and comes into contact with the first bearing 74. 【0110】 As shown in Figure 3, a first drain passage 184 is formed in the first sub-housing 18. The first drain passage 184 discharges the lubricating oil that has come into contact with the first bearing 74 from a hollow recess 118 formed by the annular protrusion 116 of the first sub-housing 18 and the resolver holder 30. Thus, the first drain passage 184 is an oil discharge passage for discharging lubricating oil to the outside of the rotating electric machine housing 14. The first drain passage 184 is also a first oil conduit that guides the lubricating oil to the gas-liquid separator 302 (described later). 【0111】 Three of each of the first oil branch passage N, first inlet 178, first secondary oil passage 180, and first oil supply hole 182 are formed. Similarly, three of the second oil branch passage R are formed. Figure 11 shows one of each of the first oil branch passage N, first inlet 178, first secondary oil passage 180, first oil supply hole 182, and second oil branch passage R. 【0112】 As described above, the outlet of the second secondary oil passage 181 is slightly bent. As a result, the outlet of the second secondary oil passage 181 faces the gap between the annular projection 380 of the oil guide member 350 and the outer surface of the first shaft portion 44a of the outer shaft 44. Therefore, a portion of the lubricating oil diverted from the first secondary oil passage 180 to the second secondary oil passage 181 is supplied from the outlet of the second secondary oil passage 181 toward the oil receiving recess 340. The lubricating oil moves from the inclined surface 342 of the oil receiving recess 340 toward the annular gap 385 between the rotating shaft 40 and the oil guide member 350. The lubricating oil that enters the annular gap 385 passes through the annular groove 384 and the first oil supply passage 386, and flows in the order of flow space 374, flow space 360, flow space 353, second oil supply passage 3582, and flow space 362. That is, the lubricating oil flows through the rotor internal oil passage 354. 【0113】 The opening of the hole in the second magnet stopper 358 (the outlet of the rotor internal oil passage 354) is covered by the disc portion 392 of the second internal stopper 90. Therefore, the lubricating oil flowing out from the rotor internal oil passage 354 comes into contact with the disc portion 392. This contact prevents the lubricating oil from flowing toward the second bearing 84. 【0114】 As shown in Figure 10, the second sub-housing 20 has a first drain hole 198, a second drain hole 197, and a second drain passage 196. Lubricating oil that flows out from the rotor internal oil passage 354 and comes into contact with the disc portion 392 flows into the second drain passage 196 via the first drain hole 198. On the other hand, lubricating oil that comes into contact with the second bearing 84 flows into the second drain passage 196 via the second drain hole 197. Thus, the second drain passage 196 is a second oil conduit that leads lubricating oil to the gas-liquid separator 302 (described later). The first drain hole 198, the second drain hole 197, and the second drain passage 196 are oil discharge passages for discharging lubricating oil to the outside of the rotating electric machine housing 14. 【0115】 As shown in Figure 10, in the second sub-housing 20, three oil receiving holes 186 are opened on the end face facing the rotating electric machine system 10. The oil receiving holes 186 are located diametrically outward from the first downstream communication holes 1681-1683. The oil receiving holes 186 are input ports for lubricating oil. 【0116】 Three third secondary oil passages 188 are provided inside the second sub-housing 20. The third secondary oil passages 188 extend radially along the diametrical direction of the second sub-housing 20. However, the third secondary oil passages 188 are formed in a phase different from that of the air relay passage 166. In addition, three oil outlet holes 190 are formed on the end face of the second sub-housing 20 facing the gas turbine engine 200. The hollow pin portion 193 of the oil distributor 192 is fitted into the oil outlet holes 190. 【0117】 Inside the oil distributor 192, a first guide passage 1941 and a second guide passage 1942 are formed. The lubricating oil that has passed through the third auxiliary oil passage 188 is divided into lubricating oil that flows through the first guide passage 1941 and lubricating oil that flows through the second guide passage 1942. The outlet of the first guide passage 1941 is located at the second proximal end 862 of the second insertion hole 86. Therefore, the lubricating oil that flows out from the first guide passage 1941 comes into contact with the second bearing 84 from the second proximal end 862. The above is another part of the first oil supply passage. 【0118】 The second guide channel 1942 branches off from the first guide channel 1941 midway. The exit of the second guide channel 1942 is connected to the second oil supply hole 195 formed in the second bearing holder 88. Therefore, the lubricating oil that has passed through the second guide channel 1942 flows out from the second oil supply hole 195 and comes into contact with the second bearing 84. 【0119】 As shown in Figure 11, the space formed by the rectifier member 96 and the second outer stopper 92 communicates with the second drain passage 196 via the second drain hole 197. Therefore, lubricating oil that enters the space flows into the second drain passage 196 through the second drain hole 197. 【0120】 As shown in Figure 12, the first drain passage 184 is connected to the gas-liquid separator 302 via the first relay pipe 3001. The second drain passage 196 is connected to the gas-liquid separator 302 via the second relay pipe 3002. The exhaust passage 172 is connected to the gas-liquid separator 302 via the third relay pipe 3003. In other words, the compressed air and lubricating oil that have flowed through the inside of the rotating electric machine housing 14 are recovered in the gas-liquid separator 302. Thus, the gas-liquid separator 302 is a recovery device for lubricating oil and compressed air, and also constitutes an oil circulation supply device. The gas-liquid separator 302 is provided with a circulation supply line 304 (circulation passage) and a discharge line 306 (discharge passage). The circulation supply line 304 is provided with a circulation pump 308, which constitutes an oil circulation supply device. 【0121】 As will be described later, the lubricating oil that flows out from the first drain passage 184 and the second drain passage 196 contains compressed air. In other words, the lubricating oil that flows into the gas-liquid separator 302 is a gas-liquid mixture. In the gas-liquid separator 302, the gas-liquid mixture is separated into lubricating oil and air. The lubricating oil is discharged from the gas-liquid separator 302 by the circulation pump 308 and resupplied to the input passage 174 via the circulation supply line 304. Meanwhile, the air is released into the atmosphere via the discharge line 306. 【0122】 Next, the gas turbine engine 200 will be described. As shown in Figure 13, the gas turbine engine 200 comprises an engine housing 202 and an output shaft 204 that rotates within the engine housing 202. The engine housing 202 includes an inner housing 2021 and an outer housing 2022. The inner housing 2021 is connected to the second sub-housing 20 of the rotating electric machine system 10. The outer housing 2022 is connected to the inner housing 2021. The outer housing 2022 is the housing body. 【0123】 As shown in Figures 1 and 10, the inner housing 2021 has a first annular portion 206, a second annular portion 208, and a plurality of legs 210. The first annular portion 206 is connected to the second sub-housing 20. The diameter of the second annular portion 208 is larger than the diameter of the first annular portion 206. The legs 210 connect the first annular portion 206 and the second annular portion 208. In the illustrated example, there are six legs 210. However, the number of legs 210 is determined according to the required coupling strength between the gas turbine engine 200 and the rotating electric machine system 10. That is, the number of legs 210 is not limited to the six shown in the illustrated example. 【0124】 A cylindrical cover portion 212 protrudes from the central opening of the second annular portion 208 toward the rotating electric machine system 10. The right end of the leg portion 210 is connected to both sides of the cylindrical cover portion 212. An intake space 214 is formed between the leg portions 210. 【0125】 As shown in Figures 10 and 13, each of the six leg portions 210 has an individual extraction passage 216. The inlet of each extraction passage 216 is formed individually at the connection point with the cylindrical cover portion 212 in the leg portion 210. The outlet of each extraction passage 216 is formed individually at the end face of the first annular portion 206 facing the second sub-housing 20. All outlets of the extraction passages 216 are located on the circumference of a virtual circle. Therefore, all outlets of the extraction passages 216 overlap with the annularly shaped collection passage 162. In other words, all of the extraction passages 216 are in communication with the collection passage 162. In this way, compressed air from the multiple extraction passages 216 flows into and collects in the collection passage 162. 【0126】 An air vent 217 is formed in the leg portion 210. The air vent 217 extends linearly from the inner wall to the outer wall of the cylindrical cover portion 212. The air vent 217 may also extend from the inner wall of the cylindrical cover portion 212 to the outer wall of the leg portion 210. There may be one or more air vents 217. Furthermore, forming an air vent 217 is not mandatory. 【0127】 As shown in Figure 13, an annular engagement recess 218 is formed on the right end face of the second annular portion 208. The engagement recess 218 positions and fixes the shroud case 220 and the diffuser 226 (described later). 【0128】 As shown in Figure 13, the gas turbine engine 200 further comprises a shroud case 220, a compressor wheel 222, a turbine wheel 224, a diffuser 226, a combustor 228, and a nozzle 230. 【0129】 The shroud case 220 is hollow and larger than the rectifier member 96. The small-diameter left end of the shroud case 220 faces the rectifier member 96. The large-diameter right end of the shroud case 220 is inserted into the cylindrical cover portion 212 of the inner housing 2021. The shroud case 220 gradually decreases in diameter from the right end to the left end, but the tip of the left end curves to expand outward in the diametrical direction. 【0130】 The left end of the shroud case 220 is exposed to the intake space 214. The top portion 102 of the rectifier member 96 enters the interior of the left end of the shroud case 220. An annular closing flange portion 232 is provided on the curved side circumferential wall of the shroud case 220. The outer edge of the closing flange portion 232 abuts against the inner walls of the cylindrical cover portion 212 and the leg portion 210. 【0131】 In the side wall of the shroud case 220, an air vent 234 is formed between the closing flange portion 232 and the first engaging projection 238. The air vent 234 extends from the inner surface to the outer surface of the side wall of the shroud case 220. The air vent 234 is the inlet to the chamber 236 when compressed air enters the chamber 236. 【0132】 Chamber 236 is interposed between the extraction port 234 and the extraction passage 216. In other words, chamber 236 connects the extraction port 234 and the extraction passage 216. Chamber 236 is also open to the atmosphere through an air vent 217. 【0133】 A first engaging projection 238 protrudes from the right end of the shroud case 220 toward the second annular portion 208. The first engaging projection 238 engages with an engaging recess 218 of the second annular portion 208. This engagement, along with the contact of the outer edge of the closing flange portion 232 against the inner walls of the cylindrical cover portion 212 and the leg portion 210, positions and fixes the shroud case 220 to the inner housing 2021. Simultaneously, a chamber 236 is formed, surrounded by the leg portion 210, the cylindrical cover portion 212 and the second annular portion 208, and the closing flange portion 232, side circumferential wall and first engaging projection 238 of the shroud case 220. The chamber 236 forms an annular shape surrounding the shroud case 220. 【0134】 The compressor wheel 222 and the turbine wheel 224 can rotate integrally with the rotating shaft 40 and the output shaft 204. Specifically, as shown in detail in Figure 5, the compressor wheel 222 has a small-diameter cylindrical portion 242 at its left end. This small-diameter cylindrical portion 242 enters into a through hole 108 formed in the flow straightening member 96. A first external spline 239 is formed on the inner wall of the small-diameter cylindrical portion 242. This first external spline 239 engages with a first internal spline 66 formed on the right open end 442 of the outer shaft 44. 【0135】 The right open end 442 of the outer shaft 44 is press-fitted into the hollow interior of the small-diameter cylindrical portion 242. As a result, the inner circumferential wall of the left opening of the small-diameter cylindrical portion 242 presses against the outer circumferential wall of the right open end 442 of the outer shaft 44 inward in the diametrical direction. The compressor wheel 222 is connected to the outer shaft 44 (rotating shaft 40) by the above-described meshing and press-fitting. 【0136】 A through-hole 240 is formed at the center of the diameter of the compressor wheel 222, extending in the left-right direction. In this through-hole 240, a second external spline 246 is engraved on the inner wall at the left end. Furthermore, in the through-hole 240, the diameter of the hole where it connects to the hollow interior of the small-diameter cylindrical portion 242 is slightly smaller than that of other parts. For this reason, an inner flange portion 248 is provided in the compressor wheel 222 near the opening of the through-hole 240 on the small-diameter cylindrical portion 242 side. In the area where the inner flange portion 248 is provided, the diameter of the through-hole 240 is at its minimum. 【0137】 The output shaft 204, provided on the turbine wheel 224, is inserted into the through hole 240. The left end of the output shaft 204 extends to approximately the same position as the left end of the small-diameter cylindrical portion 242 of the compressor wheel 222. As described above, the outer peripheral wall of the right open end 442 of the outer shaft 44 is inserted into the hollow interior of the small-diameter cylindrical portion 242. Therefore, the left end of the output shaft 204 that protrudes from the through hole 240 enters the connecting hole 62 of the rotating shaft 40. A male threaded portion 252 is engraved on the left end of the output shaft 204. The male threaded portion 252 is screwed into a female threaded portion 64 formed on the inner wall of the connecting hole 62. This screwing connects the rotating shaft 40 and the output shaft 204. 【0138】 A second internal spline 254 is formed near the left end of the output shaft 204. The second internal spline 254 engages with a second external spline 246 formed on the inner circumferential wall of the through hole 240. The left end of the output shaft 204 is press-fitted into the inner flange portion 248. 【0139】 As shown in Figure 13, a ring member 256 is interposed between the compressor wheel 222 and the turbine wheel 224. The ring member 256 is made of a heat-resistant metal material such as a nickel-based alloy. 【0140】 As shown in Figure 14, the ring member 256 has a fitting hole 258 extending from the compressor wheel 222 to the turbine wheel 224. In addition, multiple (for example, three) labyrinth-forming protrusions 264 are formed on the outer peripheral wall of the ring member 256. The labyrinth-forming protrusions 264 project outward in the diametrical direction of the ring member 256 and extend along the circumferential direction of the outer peripheral wall. As will be described later, the labyrinth-forming protrusions 264 prevent the burnt fuel (exhaust gas) generated in the combustor 228 from flowing back into the compressor wheel 222. 【0141】 In the compressor wheel 222, an annular projection 268 protrudes from the right end face facing the turbine wheel 224. When the left end face of the ring member 256 seats on the right end face of the compressor wheel 222, the annular projection 268 is fitted into the fitting hole 258. On the other hand, in the turbine wheel 224, the output shaft 204 extends from the left end face facing the compressor wheel 222. Also, a fitting projection 270 surrounding the output shaft 204 is formed on the left end face. When the right end face of the ring member 256 seats on the left end face of the turbine wheel 224, the top surface of the fitting projection 270 is fitted into the fitting hole 258. As a result, parts of the compressor wheel 222 and the turbine wheel 224 are fitted into the fitting hole 258. In this state, the ring member 256 is sandwiched between the compressor wheel 222 and the turbine wheel 224. 【0142】 The labyrinth-forming protrusion 264 is surrounded by the intermediate plate 266 inside the hollow interior of the outer housing 2022 (see Figure 13). The labyrinth-forming protrusion 264 is inserted into a hole 272 formed in the intermediate plate 266. A labyrinth flow path is formed by the inner wall of the hole 272 and the labyrinth-forming protrusion 264 in contact with this inner wall. Compressed air generated by the compressor wheel 222 reaches the labyrinth-forming protrusion 264 via the back surface of the compressor wheel 222. Meanwhile, combustion gas from the turbine wheel 224 reaches the labyrinth-forming protrusion 264. Since the pressure of the compressed air is higher than the pressure of the combustion gas, it is possible to suppress the combustion gas from passing through the labyrinth-forming protrusion 264 and flowing into the space surrounding the compressor wheel 222. 【0143】 As shown in Figure 13, within the hollow interior of the outer housing 2022, parts of the shroud case 220 and compressor wheel 222, along with the intermediate plate 266, are surrounded by the diffuser 226. A second engaging projection 273 is formed at the left end of the diffuser 226. The second engaging projection 273 engages with the engaging recess 218 together with the first engaging projection 238 of the shroud case 220. This engagement positions and fixes the diffuser 226 to the inner housing 2021. 【0144】 Inside the hollow outer housing 2022, the turbine wheel 224 is surrounded by the nozzle 230, and the nozzle 230 is surrounded by the combustor 228. An annular combustion air passage 274 is formed between the combustor 228 and the outer housing 2022. The combustion air passage 274 is a passage through which combustion air flows. A fuel supply nozzle 275 is positioned and fixed on the right end face of the outer housing 2022. The fuel supply nozzle 275 supplies fuel to the combustor 228. 【0145】 The combustor 228 has a relay hole 276 that connects the combustion air passage 274 to the inside of the combustor 228. As will be described later, the combustion air compressed by the compressor wheel 222 reaches the inside of the combustor 228 via the diffuser 226, the combustion air passage 274, and the relay hole 276. The combustor 228 also has micropores (not shown). The air discharged from the micropores forms an air curtain that cools the inside of the combustor 228. 【0146】 The nozzle 230 has a portion that surrounds the largest diameter part of the turbine wheel 224. This portion has a discharge hole (not shown) for supplying fuel, which has been burned together with the combustion air, to the turbine wheel 224. In the following, the burned fuel will also be referred to as "burned fuel." "Burned fuel" is synonymous with "combustion gas" or "exhaust gas after combustion." 【0147】 An outlet 280 is open at the right end of the outer housing 2022 and nozzle 230. The burnt fuel passes through the discharge hole and proceeds into the nozzle 230, and is then blown out of the outer housing 2022 through the outlet 280 by the rotating turbine wheel 224. Although not specifically shown in the figures, an outlet 280 is provided with an outlet pipe for discharging the burnt fuel. 【0148】 The combined power system 500 according to this embodiment is basically configured as described above. Next, the effects and advantages of the combined power system 500 will be explained. 【0149】 First, a direct current is supplied from the battery 146. The conversion circuit 152 of the current converter 150 shown in Figures 2 and 9 converts this direct current into an alternating current. The alternating current is supplied to the electromagnetic coils 110 (U-phase coil, V-phase coil, and W-phase coil) via the U-phase terminal 1441, V-phase terminal 1442, and W-phase terminal 1443. As the alternating current flows through the electromagnetic coils 110, an alternating magnetic field is generated in the stator 36. As a result, attractive and repulsive forces alternately act between the electromagnetic coils 110 and the permanent magnets 72 of the rotor 34. Consequently, the rotating shaft 40 begins to rotate. Alternatively, the rotating shaft 40 may be rotated by a known starter (not shown). 【0150】 As shown in Figure 5, a first internal spline 66 is formed on the outer peripheral wall of the right open end 442 of the outer shaft 44, and a first external spline 239 is formed on the inner wall of the small-diameter cylindrical portion 242 of the compressor wheel 222. The first internal spline 66 and the first external spline 239 mesh with each other. In addition, a second internal spline 254 is formed on the output shaft 204, and a second external spline 246 is formed on the inner wall of the through hole 240 of the compressor wheel 222. The second internal spline 254 and the second external spline 246 mesh with each other. As a result, the rotational torque of the rotating shaft 40 is quickly transmitted to the output shaft 204 via the compressor wheel 222. 【0151】 In other words, when the rotating shaft 40 starts to rotate, the output shaft 204 also starts to rotate integrally with the rotating shaft 40. Consequently, the compressor wheel 222 and turbine wheel 224, which are supported by the output shaft 204, rotate integrally with the output shaft 204. As described above, by engaging the first internal spline 66 with the first external spline 239 and engaging the second internal spline 254 with the second external spline 246, the rotational torque of the rotating shaft 40 can be sufficiently transmitted to the output shaft 204. 【0152】 Furthermore, the right end of the rotating shaft 40 is press-fitted into the hollow interior of the small-diameter cylindrical portion 242 of the compressor wheel 222. Also, the left end of the output shaft 204 is press-fitted into the inner flange portion 248 of the compressor wheel 222. As a result, the axis of the rotating shaft 40 and the axis of the output shaft 204 are precisely aligned. This effectively suppresses eccentric or vibrating rotation of the output shaft 204. 【0153】 In addition, as shown in Figure 14, a ring member 256 is interposed between the compressor wheel 222 and the turbine wheel 224. The fitting hole 258 of the ring member 256 is fitted with the annular projection 268 on the right end face of the compressor wheel 222 and the fitting projection 270 on the left end face of the turbine wheel 224. These fittings also contribute to suppressing the eccentric rotation (vibration) of the output shaft 204. Therefore, there is no need to provide a mechanism to suppress vibration. Furthermore, there is no need to increase the diameter of the output shaft 204. As a result, the combined power system 500 can be miniaturized. 【0154】 Furthermore, frictional force is generated between the right end face of the compressor wheel 222 and the left end face of the ring member 256. Frictional force is also generated between the right end face of the ring member 256 and the left end face of the turbine wheel 224. This frictional force causes the compressor wheel 222, the ring member 256, and the turbine wheel 224 to be in close contact with each other. Consequently, rotational misalignment between the two wheels 222 and 224 is prevented. 【0155】 Furthermore, when assembling the combined power system 500, the above fitting ensures that the compressor wheel 222 and turbine wheel 224 are aligned (centered) with respect to the output shaft 204. It is preferable to provide a ring member 256 between the two wheels 222 and 224, and to individually fit a portion of both wheels 222 and 224 into the fitting holes 258 of the ring member 256. This facilitates the centering of the compressor wheel 222 and turbine wheel 224 with respect to the output shaft 204. 【0156】 As a result of the above rotation, as shown in Figure 13, air is drawn into the shroud case 220 through the intake space 214 between the legs 210 of the inner housing 2021. Here, a flow straightening member 96 is located at the center of the diameter of the inner housing 2021. As described above, the flow straightening member 96 has a mountain-like shape that narrows in diameter as it approaches the shroud case 220. Moreover, the surface of the narrowed diameter portion 100 is smooth. Therefore, the air being drawn in is straightened by the flow straightening member 96 so that it is directed towards the shroud case 220. Since the right end of the flow straightening member 96 enters from the left end opening of the shroud case 220, the air is efficiently guided into the shroud case 220. In this way, by shaping the flow straightening member 96 as described above and having its top portion 102 enter into the shroud case 220, air can be efficiently collected in the shroud case 220. 【0157】 The air drawn into the shroud case 220 flows between the compressor wheel 222 and the shroud case 220. Since the space between the compressor wheel 222 and the shroud case 220 is sufficiently narrow compared to the left opening of the shroud case 220, the air is compressed during this flow. In other words, compressed air is generated. 【0158】 An air vent 234 is formed in the shroud case 220. As a result, a portion of the compressed air flows from the air vent 234 into the chamber 236. In other words, the compressed air is diverted. The chamber 236 is annular and has a larger volume than the air vent 234. Therefore, the compressed air that flows into the chamber 236 is temporarily stored in the chamber 236. 【0159】 Since multiple extraction passages 216 are formed, compressed air is distributed from the chamber 236 to each extraction passage 216. In this case, there may be pressure differences among the distributed curtain air. However, in this embodiment, the compressed air (curtain air) that has passed through the extraction port 234 flows into a single annular chamber 236. As a result, the pressure of the curtain air in the chamber 236 becomes uniform. In other words, the pressure of the curtain air is made uniform. Thus, the chamber 236 is a pressure adjustment chamber that adjusts the pressure of the curtain air to be approximately constant. 【0160】 As described above, the curtain air flowing in from the extraction port 234 is part of the compressed air and is therefore at high pressure. Here, since the volume of the chamber 236 is larger than the volume of the extraction port 234, the curtain air diffuses as it flows into the chamber 236. As a result, the pressure of the curtain air decreases. As can be understood from this, the chamber 236 also serves as a buffer chamber that reduces the pressure of the compressed air. 【0161】 The inner housing 2021 has an air vent 217 in addition to the extraction passage 216. Excess compressed air is released to the outside (atmosphere) of the gas turbine engine 200 through the air vent 217. This prevents the curtain air pressure in the chamber 236 from rising excessively. In other words, the air vent 217 allows for easy adjustment of the pressure inside the chamber 236. 【0162】 Within the chamber 236, the inlets of the extraction passages 216, each individually formed in the six legs 210, are open. Therefore, the curtain air within the chamber 236 then flows individually through the six extraction passages 216, thereby proceeding towards the second sub-housing 20. As described above, the pressure of the curtain air is approximately constant at this point. 【0163】 As shown in Figure 10, the outlets of all six extraction passages 216 overlap with the collection passage 162. Therefore, the curtain air that has flowed through the six extraction passages 216 flows into the collection passage 162, collects there, and diffuses in an annular pattern along the collection passage 162. In this process, the pressure of the curtain air is further homogenized. 【0164】 The curtain air then flows individually from the collective channel 162 into three upstream communication holes 164 and flows individually along three air relay paths 166. Subsequently, a portion of the curtain air is discharged from the first downstream communication holes 1681-1683. The remaining portion of the curtain air is discharged from the second downstream communication holes 1701-1703. Hereafter, the curtain air discharged from the first downstream communication holes 1681-1683 will be referred to as the "first branch air," and the curtain air discharged from the second downstream communication holes 1701-1703 will be referred to as the "second branch air." 【0165】 The path of the first branch air will now be described. The first downstream communication hole 1681 communicates with the hollow interior of the first hollow pipe section 1601. The first downstream communication hole 1682 communicates with the hollow interior of the second hollow pipe section 1602. The first downstream communication hole 1683 communicates with the hollow interior of the third hollow pipe section 1603. Therefore, the first branch air flows through the hollow interiors of the first hollow pipe section 1601 to the third hollow pipe section 1603 as shown in Figure 1, etc., and proceeds from the second end to the first end of the rotating electric machine housing 14. 【0166】 The first hollow tube section 1601 to the third hollow tube section 1603 are located on the outer periphery of the cooling jacket 24. A cooling medium is pre-circulated in the cooling jacket 24. Therefore, as the first branch air flows along the first hollow tube section 1601 to the third hollow tube section 1603, the heat from the first branch air is sufficiently conducted to the cooling medium. As a result, the first branch air becomes relatively cold. In other words, in this embodiment, the first branch air can be cooled by the cooling jacket 24, which is used to cool the rotating electric machine 12 and the current converter 150, etc. 【0167】 For the reasons stated above, there is no need to provide separate cooling equipment for cooling the curtain air in the gas turbine engine 200 or the rotating electric machine system 10. Therefore, the combined power system 500 can be made smaller. 【0168】 The first diverted air that has flowed through the first hollow pipe section 1601 flows into the second internal space of the second casing 28, as shown in Figure 2. This forms an air curtain inside the second casing 28. The excess first diverted air flows into the first internal space 29 of the first casing 26 through the interconnection holes. 【0169】 The first branch air that has flowed through the second hollow pipe section 1602 and the third hollow pipe section 1603 flows into the first internal space 29 of the first casing 26. Therefore, an air curtain is formed in the first internal space 29 by the first branch air that has flowed through the first hollow pipe sections 1601 to the third hollow pipe sections 1603. 【0170】 As shown in Figure 3, the excess first branch air flows from the first internal space 29 into the storage chamber 22 of the main housing 16. As can be understood from this, the first internal space 29 and the second internal space are located upstream in the flow direction of the first branch air. In other words, the storage chamber 22 and the rotating electric machine 12 are located downstream of the first casing 26 and the second casing 28 in the flow direction of the first branch air. 【0171】 The first casing 26 and the second casing 28 are located at the first end (left end) of the main housing 16. Therefore, the first branch air flows in from the left end of the storage chamber 22. The first branch air then enters the clearance between the outer circumferential wall of the cylindrical projection 76 and the insulating substrate 112. This clearance is the inner bore of the stator 36. 【0172】 A portion of the first branched air then flows towards the first insertion hole 78 via the first air branch L. The remaining portion of the first branched air flows towards the second insertion hole 86 via the second air branch M, along the clearance between the outer wall of the permanent magnet 72 and the inner wall of the electromagnetic coil 110. In this way, the first branched air is divided into compressed air heading towards the first insertion hole 78 at the left end (first end) and compressed air heading towards the second insertion hole 86 at the right end (second end). 【0173】 The rotating electric machine 12 is cooled as the first branch air flows along the clearance between the outer wall of the permanent magnet 72 and the inner wall of the electromagnetic coil 110. Here, as described above, the first branch air is sufficiently cooled by the cooling jacket 24. Therefore, the rotating electric machine 12 is cooled efficiently. 【0174】 Furthermore, in this embodiment, the rotating electric machine 12 is cooled using compressed air generated by the gas turbine engine 200. Therefore, there is no need to supply cooling air to the storage chamber 22 to cool the rotating electric machine 12. This makes it possible to simplify the configuration of the combined power system 500 while cooling the rotating electric machine 12. 【0175】 A portion of the first branched air that flows toward the first insertion hole 78 reaches the first proximal end 782 of the first insertion hole 78. At this first proximal end 782, a portion of the first branched air forms an air curtain for the first bearing 74. Meanwhile, the remaining portion of the first branched air that flows toward the second insertion hole 86 reaches the second distal end 861 of the second insertion hole 86 via the third sub-branch 941. At this second distal end 861, the remaining portion of the first branched air forms an air curtain for the second bearing 84. 【0176】 The path of the second branch air will now be described. The second downstream communication holes 1701 to 1703 each individually overlap with three inlets 104 formed in the base portion 98 of the flow straightening member 96. Therefore, the second branch air flows into the relay chamber 106 (the hollow interior of the flow straightening member 96) via the inlets 104. 【0177】 As described above, the outlet of the relay chamber 106 opens at a position facing the small-diameter cylindrical portion 242 of the compressor wheel 222. Therefore, the second branched air flowing into the relay chamber 106 comes into contact with the small-diameter cylindrical portion 242. A portion of the second branched air then flows toward the fourth sub-branch 942. The remainder of the second branched air flows toward the outlet 943. 【0178】 A portion of the second branch air reaches the second proximal end 862 of the second insertion hole 86 via the fourth sub-branch 942. At this second proximal end 862, a portion of the second branch air forms an air curtain for the second bearing 84. In this way, the second bearing 84 is sandwiched between the remaining portion of the second branch air that reached the second proximal end 862 and a portion of the first branch air that reached the second distal end 861. 【0179】 The remaining portion of the second branch air is discharged into the left end of the shroud case 220 via the outlet passage 943. As described above, intake air is drawn in at the left end opening of the shroud case 220. Therefore, the remaining portion of the second branch air is compressed by the compressor wheel 222 together with the drawn-in atmosphere. 【0180】 The excess first branch air reaches the exhaust passage 172 via the storage chamber 22. The excess second branch air flows from the second end to the first end of the main housing 16, for example, through the clearance between the inner wall of the storage chamber 22 and the electromagnetic coil 110. Subsequently, the excess second branch air reaches the exhaust passage 172. The first and second branch air that reach the exhaust passage 172 are recovered by the gas-liquid separator 302 (recovery device) via the third relay pipe 3003. 【0181】 As described above, the pressure of the curtain air is made uniform by the chamber 236 provided between the inner housing 2021 and the shroud case 220. Therefore, pressure distribution in the curtain air is avoided. Furthermore, surging in the curtain air is also avoided. As a result, it is possible to supply the curtain air around the first bearing 74 and the second bearing 84 while maintaining the curtain air pressure at a substantially constant level. 【0182】 As described above, the relay chamber 106 widens as it approaches the fourth sub-branch 942. Moreover, the second branch air flowing out of the relay chamber 106 is divided into a portion that goes towards the fourth sub-branch 942 and the remainder that goes towards the exit channel 943. Consequently, the pressure of the second branch air reaching the second proximal end 862 is lower than the pressure of the second branch air before it flowed into the relay chamber 106. As a result, the pressure of the first branch air reaching the second distal end 861 and the pressure of the second branch air reaching the second proximal end 862 are in equilibrium. 【0183】 Next, the lubrication oil pathway will be described. A portion of the lubrication oil is supplied to the first bearing 74 and the second bearing 84 as a lubricant. The remaining portion of the lubrication oil is supplied to the rotating shaft 40 as a cooling oil to cool the rotating electric machine 12. 【0184】 The lubricating oil that has flowed through the first drain passage 184 and the second drain passage 196 is recovered in the gas-liquid separator 302 shown in Figure 12. In the gas-liquid separator 302, the lubricating oil is separated from the compressed air (curtain air). The lubricating oil is then pushed out by the circulation pump 308. The lubricating oil is supplied to the input passage 174 formed in the main housing 16 via the circulation supply line 304. The lubricating oil flows from the input passage 174 into the main oil passage 176. The main oil passage 176 branches into a first oil branch passage N leading to the first sub-housing 18 and a second oil branch passage R leading to the second sub-housing 20. Therefore, the lubricating oil is divided into lubricating oil flowing along the first oil branch passage N and lubricating oil flowing along the second oil branch passage R. 【0185】 A portion of the lubricating oil flows into the first auxiliary oil passage 180 through a first inlet hole 178 formed in the first sub-housing 18. A portion of the lubricating oil flowing through the first auxiliary oil passage 180 further flows from the first auxiliary oil passage 180 into the second auxiliary oil passage 181. Hereinafter, the lubricating oil that flows along the first auxiliary oil passage 180 and is discharged from the outlet of the first auxiliary oil passage 180 will be referred to as the "first branch oil." The lubricating oil that flows along the second auxiliary oil passage 181 and is discharged from the outlet of the second auxiliary oil passage 181 will be referred to as the "cooling oil." The lubricating oil that flows along the second oil branch passage R will be referred to as the "second branch oil." 【0186】 The first branched oil discharged from the outlet of the first auxiliary oil passage 180 is supplied to the first distal end 781 of the first insertion hole 78 through the first oil supply hole 182 formed in the first bearing holder 80. At this time, the first branched oil is guided by the upstream guide groove 390 of the oil guide member 350 and the downstream guide groove 368 formed in the first outer stopper 81 toward the first bearing 74. The first branched oil further enters the inner bore of the first bearing 74 and lubricates the first bearing 74. 【0187】 The first branching oil that flows from the first distal end 781 to the first proximal end 782 is blocked by the first branching air (air curtain) that reaches the first proximal end 782. Therefore, the first branching oil is prevented from flowing toward the first air branching path L. As a result, the first branching oil is also prevented from entering between the rotating shaft 40 and the electromagnetic coil 110. This prevents the rotating electric machine 12 from being contaminated with the first branching oil. 【0188】 The excess first flow oil flows into the hollow recess 118. The first drain passage 184 is connected to the hollow recess 118. Therefore, the first flow oil in the hollow recess 118 is recovered by the gas-liquid separator 302 via the first drain passage 184. 【0189】 The second branched oil, having flowed through the second oil branch channel R, flows into the third auxiliary oil channel 188 through the oil receiving hole 186 formed in the second sub-housing 20. The second branched oil, having flowed through the third auxiliary oil channel 188, is divided into the first guide channel 1941 and the second guide channel 1942 formed inside the oil distributor 192. A portion of the second branched oil that flows out from the outlet of the first guide channel 1941 is supplied to the second proximal end 862 of the second insertion hole 86. The remainder of the second branched oil that has passed through the second guide channel 1942 is supplied to the second bearing 84 through the second oil supply hole 195 formed in the second bearing holder 88. The second branched oil enters the inner bore of the second bearing 84 and lubricates the second bearing 84. 【0190】 The second branching oil that enters the inner bore of the second bearing 84 is surrounded by the first branching air supplied to the second distal end 861 and the second branching air supplied to the second proximal end 862. As described above, the pressure of the first branching air supplied to the second distal end 861 and the pressure of the second branching air supplied to the second proximal end 862 are in equilibrium. Therefore, the flow of the second branching oil toward the third sub-branch 941 or the fourth sub-branch 942 is prevented. As a result, the second branching oil is prevented from entering between the rotating shaft 40 and the electromagnetic coil 110. Furthermore, the second branching oil is prevented from entering the relay chamber 106 of the flow straightening member 96. This prevents the rotating electric machine 12 and the flow straightening member 96 from being contaminated with the second branching oil. 【0191】 As described above, the pressure of the curtain air is adjusted to be approximately constant. Therefore, an air curtain of a predetermined pressure is continuously formed around the first bearing 74 and the second bearing 84. This prevents lubricating oil from leaking from the first bearing 74 and the second bearing 84. 【0192】 The excess second branch oil flows into the space formed by the flow straightening member 96 and the second outer stopper 92. The second sub-housing 20 has a second drain hole 197 and a second drain passage 196. The second branch oil that flows into the space is collected by the gas-liquid separator 302 via the second drain hole 197 and the second drain passage 196. 【0193】 As described above, the first branch oil lubricates the first bearing 74, and the second branch oil lubricates the second bearing 84. This prevents seizure from occurring in the first bearing 74 and the second bearing 84. 【0194】 The path of the cooling oil flowing through the second secondary oil passage 181 will now be described. As described above, the outlet of the second secondary oil passage 181 faces the annular gap 385 between the annular projection 380 of the oil guide member 350 and the outer surface of the first shaft portion 44a of the outer shaft 44 (see Figures 7 and 8). Therefore, as shown in Figures 7 and 8, the cooling oil is discharged from the outlet of the second secondary oil passage 181 toward the annular gap 385. 【0195】 The inclined surface 342 of the oil receiving recess 340 is inclined so as to roughly coincide with the direction of travel of the cooling oil discharged from the outlet of the second sub-oil passage 181. Therefore, the cooling oil discharged from the outlet of the second sub-oil passage 181 efficiently contacts the inclined surface 342 and moves toward the bottom surface 346 of the oil receiving recess 340. 【0196】 At this point, the rotating shaft 40 has started to rotate. Therefore, the lubricating oil that has entered the oil receiving recess 340 moves to the annular groove 384 located on the outer circumference of the oil receiving recess 340 due to the action of centrifugal force. Since the oil receiving recess 340 and the annular groove 384 have sufficient volume, it is possible to temporarily store a predetermined amount of cooling oil in the oil receiving recess 340 and the annular groove 384. 【0197】 The annular groove 384 communicates with the annular space 388 shown in Figure 8 via a first oil supply passage 386 formed in the annular projection 382 of the oil guide member 350. The annular space 388 communicates with the rotor internal oil passage 354. Therefore, the cooling oil flows into the rotor internal oil passage 354 via the annular space 388. The cooling oil then flows through the rotor internal oil passage 354 toward the first drain hole 198. 【0198】 During this flow process, the cooling oil passes through the first stage 330, the second stage 332, the third stage 334, and the fourth stage 336 (see Figure 6). As a result, the cooling oil moves smoothly outward in the diametrical direction of the rotating shaft 40 as it moves from upstream to downstream in the flow direction of the cooling oil. Thus, when the cooling oil passes through the first stage 330, the second stage 332, the third stage 334, and the fourth stage 336, it flows along a direction other than the axial direction of the rotating shaft 40. In other words, the first stage 330, the second stage 332, the third stage 334, and the fourth stage 336 are direction-changing sections that change the flow direction of the cooling oil to a direction outward in the diametrical direction of the rotating shaft 40. The direction-changing section has multiple stages arranged at intervals in the axial direction of the rotating shaft 40, namely the first stage 330, the second stage 332, the third stage 334, and the fourth stage 336. At least one of the multiple stepped sections (in this embodiment, the third stepped section 334) is located inside the annularly arranged permanent magnet 72. At least one of the multiple stepped sections (in this embodiment, the first stepped section 330, the second stepped section 332, and the fourth stepped section 336) is provided in a position exposed from the permanent magnet 72 in the axial direction of the rotating shaft 40. 【0199】 As the rotating shaft 40 rotates, centrifugal force acts on the cooling oil flowing through the rotor's internal oil passage 354. This centrifugal force causes the cooling oil to tend to move outward in the diametrical direction of the rotating shaft 40. As described above, the outer shaft 44 constituting the rotating shaft 40 is provided with a direction-changing section based on the first stage 330, the second stage 332, the third stage 334, and the fourth stage 336. This direction-changing section directs the cooling oil outward in the diametrical direction of the rotating shaft 40. 【0200】 The coolant flowing along the direction change section is subjected to a force acting outward in the diametrical direction of the rotating shaft 40 and a force acting axially on the rotating shaft 40. Therefore, the coolant tends to flow in the direction of the combined force of these two forces. This prevents the coolant from being concentrated on the inner circumferential wall of, for example, the inner bore 73 of the cylindrical member 70. Consequently, obstruction of the coolant flow due to such uneven distribution is avoided. 【0201】 In other words, based on the formation of a direction-changing section on the outer shaft 44 of the rotating shaft 40, the cooling oil flows smoothly along the axial direction of the rotating shaft 40 while moving outward in the diametrical direction of the rotating shaft 40. That is, even though centrifugal force acts on the cooling oil, the cooling oil can be made to flow along the axial direction of the rotating shaft 40. 【0202】 As the cooling oil flows through the internal oil passage 354 of the rotor, it comes into contact with the outer surface of the outer shaft 44. As a result, the outer shaft 44 is cooled. At the same time, the cooling oil comes into contact with the inner circumferential wall of the inner bore 73 of the cylindrical member 70. Consequently, the cylindrical member 70 and the permanent magnet 72 are cooled. In this way, an excessive rise in the temperature of the rotor 34 is suppressed. 【0203】 In other words, the temperature rise of the permanent magnet 72 is suppressed by the cooling provided by the first branch air and cooling oil. Therefore, the temperature of the permanent magnet 72 is prevented from reaching the Curie temperature. As a result, the reduction in the magnetic force of the permanent magnet 72 can be suppressed. Consequently, a predetermined magnetic force is generated in the alternating magnetic field formed between the permanent magnet 72 and the electromagnetic coil 110. This allows the rotating electric machine 12 to maintain a predetermined output. Furthermore, it is possible to increase the output by rotating the rotor 34 at high speed. 【0204】 Cooling oil that flows out from the outlet (flow space 362) of the rotor oil passage 354 comes into contact with the disc portion 392. As shown in Figure 11, the cooling oil flows into the second drain passage 196 through the first drain hole 198 formed in the second sub-housing 20. In the second drain passage 196, the cooling oil merges with the second branched oil and is then recovered by the gas-liquid separator 302. 【0205】 As can be understood from this, the disc portion 392 prevents the coolant from moving toward the second bearing 84. Therefore, even if dust or other particles are mixed in the coolant, it is prevented from reaching the second bearing 84. In addition, it is prevented the coolant, whose temperature has risen as it flows through the rotor oil passage 354, from coming into contact with the second bearing 84. Therefore, it is prevented the temperature of the second bearing 84 from rising excessively. 【0206】 As described above, the first and second branch air (curtain air), the first branch oil, the second branch oil, and the cooling oil (lubricating oil) are recovered in the gas-liquid separator 302. Here, the lubricating oil is blocked by an air curtain inside the rotating electric machine housing 14. For this reason, the curtain air exhausted from the exhaust passage 172 contains lubricating oil. In other words, the curtain air exhausted from the exhaust passage 172 is essentially a gas-liquid mixture. 【0207】 In this embodiment, the oil circulation supply device includes a gas-liquid separator 302. Thus, the gas-liquid mixture is separated into air and lubricating oil. The air is released into the atmosphere via a discharge line 306 provided in the gas-liquid separator 302. Meanwhile, the lubricating oil is pushed out of the gas-liquid separator 302 by a circulation pump 308. The lubricating oil is further resupplied from the gas-liquid separator 302 to the first bearing 74 and the second bearing 84 via a circulation supply line 304. While the rotating shaft 40 rotates, the first bearing 74, the second bearing 84 and the rotor 34 are cooled by the lubricating oil. 【0208】 In this way, by separating the gas-liquid mixture into lubricating oil and air in the gas-liquid separator 302, so-called air entrapment is avoided in the circulation supply line 304 and the circulation pump 308. Therefore, lubricating oil can be resupplied to the first bearing 74 and the second bearing 84 at an appropriate discharge pressure or flow rate. As a result, the first bearing 74 and the second bearing 84 are sufficiently lubricated. Consequently, seizure of the first bearing 74 and the second bearing 84 can be suppressed. 【0209】 Furthermore, air curtains are formed in the second air branch M, the third sub-branch 941, and the fourth sub-branch 942. These air curtains prevent lubricating oil from entering the first internal space 29 and the second internal space. Consequently, the adhesion of lubricating oil to the U-phase terminal 1441, V-phase terminal 1442, W-phase terminal 1443, and thermistor 148 is suppressed. In other words, contamination of electrical terminals and measuring instruments (thermistor 148), etc., with lubricating oil can be avoided. 【0210】 As described above, the curtain air (first and second branch air) prevents lubricating oil from scattering from the first bearing 74 and the second bearing 84. The curtain air is then discharged to the outside of the rotating electric machine housing 14 as described above. Therefore, even if lubricating oil leaks from the first bearing 74 or the second bearing 84, the leaked lubricating oil is carried by the curtain air and discharged to the outside of the rotating electric machine housing 14. Thus, it is possible to prevent the leaked lubricating oil from flowing toward the rotor 34. Furthermore, it is possible to prevent the leaked lubricating oil from remaining inside the rotor 34. 【0211】 As described above, the pressure of the curtain air continuously supplied to the rotating electric machine housing 14 is approximately constant. Therefore, it is possible to continuously prevent the scattering of lubricating oil. Furthermore, even if lubricating oil leaks, the leaked lubricating oil can be continuously discharged to the outside of the rotating electric machine housing 14. 【0212】 The compressed air that passes between the shroud case 220 and the compressor wheel 222 without entering the extraction port 234 becomes combustion air. As shown in Figure 13, the combustion air flows into the diffuser 226. The combustion air flows out from the outlet hole formed in the wall of the diffuser 226 into the combustion air passage 274 between the combustor 228 and the outer housing 2022. The combustion air then flows into the combustion chamber (the hollow interior of the combustor 228) through the intermediate hole 276 formed in the combustor 228, the aforementioned micropores, and the clearance between the combustor 228 and the fuel supply nozzle 275. 【0213】 The combustor 228 is preheated. Consequently, the combustion chamber is also at a high temperature. Fuel is supplied to the high-temperature combustion chamber from the fuel supply nozzle 275. The fuel burns together with the combustion air, becoming high-temperature burnt fuel. When this burnt fuel is supplied into the nozzle 230 from the discharge hole, it expands within the nozzle 230. This causes the turbine wheel 224 to start rotating at high speed. 【0214】 The output shaft 204 holds the turbine wheel 224. A compressor wheel 222 is also provided on the output shaft 204. Therefore, as the turbine wheel 224 rotates at high speed, the output shaft 204 and the compressor wheel 222 rotate together at high speed. Simultaneously, the rotating shaft 40 also rotates at high speed. The burnt fuel is discharged outside the outer housing 2022 through a discharge pipe (not shown) provided at the discharge port 280. 【0215】 The ring member 256 interposed between the compressor wheel 222 and the turbine wheel 224 also serves as a sealing member that seals the space between the two wheels 222 and 224. Furthermore, as shown in Figure 14, multiple labyrinth-forming protrusions 264 are formed on the outer peripheral wall of the ring member 256. These labyrinth-forming protrusions 264 abut against the inner wall of the hole 272 formed in the intermediate plate 266. Compressed air generated by the compressor wheel 222 reaches the labyrinth-forming protrusions 264 via the back surface of the compressor wheel 222. Combustion gas from the turbine wheel 224 also reaches the labyrinth-forming protrusions 264. As described above, the pressure of the compressed air is higher than the pressure of the combustion gas. Therefore, the flow of combustion gas through the labyrinth-forming protrusions 264 into the compressor wheel 222 is suppressed. For the reasons stated above, it is prevented, for example, from entering the through-hole 240 from between the two wheels 222 and 224. 【0216】 In Figure 13, when the output shaft 204 starts rotating at high speed, the current supply from the battery 146 (see Figure 9) to the electromagnetic coil 110 is stopped. However, as described above, since the turbine wheel 224 is already rotating at high speed, the rotating shaft 40 rotates at high speed together with the turbine wheel 224 and the output shaft 204. At this time as well, for the same reasons as described above, sufficient rotational torque is transmitted from the output shaft 204 to the rotating shaft 40. 【0217】 In Figure 3, it is preferable that the rotation direction of the output shaft 204 and the rotating shaft 40 is opposite to the rotation direction when the small cap nut 58, the large cap nut 60, and the male threaded portion 252 are screwed together. In this case, loosening of the small cap nut 58, the large cap nut 60, and the male threaded portion 252 during the rotation of the rotating shaft 40 is avoided. Alternatively, a mechanism to prevent loosening may be provided on the small cap nut 58, the large cap nut 60, or the male threaded portion 252. 【0218】 Since the rotating shaft 40 holds the permanent magnet 72, an alternating current is generated in the electromagnetic coil 110 surrounding the permanent magnet 72. The alternating current is sent to the current converter 150 shown in Figures 2 and 9 via the U-phase terminal 1441, V-phase terminal 1442, and W-phase terminal 1443. The conversion circuit 152 of the current converter 150 converts this alternating current into a direct current. When the control circuit 156 of the current converter 150 determines that the output of an external load (e.g., a motor) electrically connected to the battery 146 has decreased, it supplies a direct current to the battery 146 (see Figure 9) via the capacitor 154. This charges the battery 146. 【0219】 During this process, the current converter 150, particularly the conversion circuit 152 and the capacitor 154, becomes heated. However, in this embodiment, the conversion circuit 152 and the capacitor 154 inside the equipment case 158 are in close proximity to the cooling jacket 24. Therefore, the heat from the conversion circuit 152 and the capacitor 154 is quickly conducted to the cooling medium inside the cooling jacket 24. This prevents the conversion circuit 152 and the capacitor 154 from becoming excessively hot. 【0220】 The electromagnetic coil 110 generates heat as current flows through it. At this point, a portion of the first branch air comes into contact with the left end of the stator 36. In addition, the remaining portion of the first branch air, which flows through the storage chamber 22 towards the second insertion hole 86, comes into contact with the outer and inner walls of the stator 36. As a result, the stator 36 is cooled by the first branch air. Furthermore, a cooling medium flows through the cooling jacket 24 provided in the main housing 16. The rotating electric machine 12 is rapidly cooled by this cooling medium. This also allows a predetermined magnetic force to be generated in the alternating magnetic field formed between the permanent magnet 72 and the electromagnetic coil 110. 【0221】 In this embodiment, a rotating electric machine housing 14 (main housing 16) housing the rotating electric machine 12 and a first casing 26 housing the U-phase terminal 1441, V-phase terminal 1442, and W-phase terminal 1443 are provided separately. Therefore, the heat generated in the stator 36 inside the main housing 16 is less likely to affect the U-phase terminal 1441, V-phase terminal 1442, and W-phase terminal 1443 inside the first casing 26. However, the U-phase terminal 1441, V-phase terminal 1442, and W-phase terminal 1443 also generate heat when energized. Nevertheless, the U-phase terminal 1441, V-phase terminal 1442, and W-phase terminal 1443 are rapidly cooled by the first branch air supplied to the first casing 26. 【0222】 Thus, the first branch air also serves to cool the heat-generating parts in the rotating electric machine system 10. Since the electrical terminals (U-phase terminal 1441, V-phase terminal 1442, and W-phase terminal 1443), electromagnetic coil 110, and permanent magnet 72 are cooled, the effects of heat on the output control of the rotating electric machine system 10 are avoided. Furthermore, the excitation of the electromagnetic coil 110 and permanent magnet 72, etc., which may be reduced due to heat are also avoided. As a result, the reliability of the rotating electric machine system 10 is improved. 【0223】 Furthermore, since the main housing 16 that houses the rotating electric machine 12 and the first casing 26 that houses the U-phase terminal 1441, V-phase terminal 1442, and W-phase terminal 1443 are provided separately, the rotating electric machine 12 and the electrical terminal section are spaced apart from each other. As a result, the U-phase terminal 1441, V-phase terminal 1442, and W-phase terminal 1443 are less susceptible to vibrations generated as the rotor 34 rotates. In other words, the U-phase terminal 1441, V-phase terminal 1442, and W-phase terminal 1443 are protected from vibrations. Also, as described above, the occurrence of seizure in the first bearing 74 and the second bearing 84 is suppressed by the lubricating oil. Therefore, the rotating electric machine system 10 has excellent durability. 【0224】 While the rotating shaft 40 is rotating, the rotation angle (rotation parameter) of the rotating shaft 40 is detected by the resolver 132. Specifically, the resolver rotor 56, which is fitted onto the left end 422 of the inner shaft 42, rotates integrally with the rotating shaft 40. As a result, the electrical signal generated in the resolver stator 130 is transmitted to the receiver via the transmission connector 136. The receiver, having read the electrical signal, calculates the rotation angle of the rotating shaft 40 based on the electrical signal. The receiver sends the calculation result to a control device (not shown). The control device calculates the rotation speed based on this rotation angle. 【0225】 The resolver 132 is positioned on the protruding tip 46 of the rotating shaft 40, which is exposed from the rotating electric machine housing 14. Therefore, the resolver 132 is less affected by the heat generated in the electromagnetic coil 110 of the stator 36 inside the rotating electric machine housing 14. Furthermore, the resolver 132 is less affected by vibrations generated as the rotor 34 rotates. In addition, the first bearing 74 and the second bearing 84 that support the rotating shaft 40 are located inside the rotating electric machine housing 14. Therefore, the vibration of the first bearing 74 and the second bearing 84 is suppressed by the rotating electric machine housing 14. This also makes it difficult for vibrations to affect the resolver 132. 【0226】 As described above, in this embodiment, the transmission of heat and vibration to the resolver 132 is suppressed. This results in more accurate detection of the rotation angle by the resolver 132. Furthermore, the lifespan of the resolver 132 is extended. 【0227】 It may be necessary to replace resolver 132 with another resolver having a larger inner and outer diameter. If a single solid rotating shaft is used as the rotating shaft, replacing it with a resolver with a larger inner and outer diameter requires replacing it with a larger diameter solid rotating shaft. In this case, it is not easy to pass the larger diameter solid rotating shaft through the first bearing 74 and the second bearing 84. 【0228】 In this embodiment, the rotating shaft 40 is composed of an outer shaft 44 and an inner shaft 42. The outer shaft 44 passes through the first bearing 74 and the second bearing 84, and a resolver rotor 56 is provided on the portion of the inner shaft 42 that is exposed from the outer shaft 44. Therefore, when replacing the resolver 132 with another resolver with a larger inner and outer diameter, this can be done by replacing the inner shaft 42 with an inner shaft having a larger diameter at its left end 422. As can be seen from this, according to this embodiment, by replacing the inner shaft 42, it is possible to accommodate resolvers with various inner and outer diameters. 【0229】 In this embodiment, a third sub-branch 941 and a fourth sub-branch 942 are provided. Alternatively, the first air branch L may be branched into a first sub-branch and a second sub-branch. In this case, a portion of the first divided air is supplied from the first sub-branch to the first distal end 781, and a portion of the first divided air is supplied from the second sub-branch to the first proximal end 782. Alternatively, the first air branch L may be branched into a first sub-branch and a second sub-branch, and a third sub-branch 941 and a fourth sub-branch 942 may be provided. 【0230】 In the gas turbine engine 200, the compressor wheel 222 and the turbine wheel 224 can be arranged in the opposite configuration to that shown in Figure 13. In this case, a through hole 240 can be formed in the turbine wheel 224, and an output shaft 204 can be provided in the compressor wheel 222. In addition, the compressor wheel 222 and the turbine wheel 224 may be of the centrifugal or axial flow type. If the compressor wheel 222 and the turbine wheel 224 are arranged on the same axis, a combination of a centrifugal and an axial flow type multi-stage compressor wheel and a multi-stage turbine wheel is also acceptable. 【0231】 In Figure 3, the rotating electric machine 12 constituting the rotating electric machine system 10 may be a motor in which the rotating shaft 40 rotates when the electromagnetic coil 110 is energized. In this case, the U-phase terminal 1441, V-phase terminal 1442, and W-phase terminal 1443 become electrical terminals that receive power from the battery 146. 【0232】 The rotating electric machine system 10 can also be separated from the gas turbine engine 200 and used independently. If it is necessary to supply compressed air to the rotating electric machine system 10, a compression pump 320 may be provided outside the rotating electric machine housing 14, as shown in Figure 15, and this compression pump 320 may be used as an air supply device. 【0233】 In this case, for example, a flow hole 322 is formed in the first casing 26. Compressed air supplied from the compression pump 320 flows into this flow hole 322. In addition, a connecting hole 324 connected to the upstream communication hole 164 is formed in the second sub-housing 20. The connecting hole 324 is closed with a plug 326. In this state, compressed air is obtained by the compression pump 320 compressing the atmosphere or the like. This compressed air is supplied to the first hollow pipe section 1601 to the third hollow pipe section 1603. 【0234】 Furthermore, in the above embodiment, the cooling oil is circulated in the direction from the first bearing 74 to the second bearing 84, but conversely, the cooling oil may be circulated in the direction from the second bearing 84 to the first bearing 74. In this case, the second sub-oil passage 181 is branched from the third sub-oil passage 188. Also, it is preferable to increase the outer diameter of the outer shaft 44 as it moves from the second bearing 84 to the first bearing 74. The disc portion 392 is provided at the second end of the first inner stopper 82. 【0235】 Instead of providing the disc portion 392 on the first inner stopper 82 or the second inner stopper 90, a separate disc member may be attached to the outer shaft 44. 【0236】 As described above, this embodiment is a rotating electric machine system (10) comprising a rotating electric machine (12) having a rotor (34) including a permanent magnet (72) and a rotating shaft (40), and a rotating electric machine housing (14) that rotatably supports the rotating shaft, wherein the rotating electric machine system (10) comprises a first bearing (74) and a second bearing (84) interposed between the rotating electric machine housing and the rotating shaft, and an oil circulation supply device that circulates and supplies lubricating oil to the first bearing and the second bearing, and the rotating electric machine housing is supplied with oil from the oil circulation supply device. The disclosed rotating electric machine system includes a first oil supply passage (176) for supplying the lubricating oil to the first bearing and the second bearing, and a second oil supply passage (181) branching off from the first oil supply passage and supplying the lubricating oil toward the rotor, wherein an internal rotor oil passage (354) is formed inside the rotor for circulating the lubricating oil that has flowed out from the second oil supply passage, and the rotating electric machine housing has oil discharge passages (184, 196) for discharging the lubricating oil that has flowed through the first oil supply passage, the second oil supply passage and the internal rotor oil passage to the oil circulation supply device. 【0237】 In this embodiment, a portion of the lubricating oil supplied to the bearings is diverted and circulated through the oil passages within the rotor. Based on this circulation, the rotor, which constitutes the rotating electric machine, is efficiently cooled by the lubricating oil. 【0238】 As can be understood from this, in this embodiment, a portion of the lubricating oil is used as cooling oil to cool the rotor. Therefore, it is not necessary to provide separate oil passages for supplying and recovering lubricating oil for the bearings and for supplying and recovering cooling oil for the rotor. This eliminates concerns about the configuration of the rotating electric machine system becoming complex. It also eliminates concerns about the rotating electric machine system becoming large. 【0239】 Furthermore, since the rotor is cooled by lubricating oil, the temperature of the permanent magnets constituting the rotor is prevented from reaching the Curie temperature. Therefore, the reduction in the magnetic force of the permanent magnets is suppressed. As a result, a predetermined magnetic force is generated in the alternating magnetic field formed between the permanent magnets and the electromagnetic coil. This allows the rotating electric machine to maintain a predetermined output. Additionally, it is possible to increase the output by rotating the rotor at high speed. 【0240】 This embodiment discloses a rotating electric machine system in which the rotor has a cylindrical member (70) interposed between the rotating shaft and the permanent magnet in the diametrical direction of the rotating shaft, and at least a portion of the oil passage inside the rotor is formed between the outer surface of the rotating shaft and the inner circumferential wall of the cylindrical member. 【0241】 This makes it possible to easily form a portion of the oil passages inside the rotor. 【0242】 This embodiment discloses a rotating electric machine system in which the oil passages within the rotor are spaces that extend along the axial direction of the rotating shaft. 【0243】 This allows the rotor to be cooled along its entire axial direction. 【0244】 This embodiment discloses a rotating electric machine system in which the oil passages within the rotor extend at least from one end to the other of the permanent magnet in the axial direction of the rotating shaft. 【0245】 In this case, the entire permanent magnet is cooled efficiently. Therefore, the rise in the temperature of the permanent magnet can be further suppressed. 【0246】 This embodiment discloses a rotating electric machine system in which the inlet of the rotor oil passage is located outward from the first bearing in the axial direction of the rotating shaft, and the outlet of the rotor oil passage is located inward from the second bearing in the axial direction of the rotating shaft. 【0247】 This prevents the lubricating oil supplied to the first bearing from flowing through the oil passages inside the rotor. Similarly, it prevents the lubricating oil that has flowed through the oil passages inside the rotor from being supplied to the second bearing. 【0248】 This embodiment discloses a rotating electric machine system in which the first oil supply passage has a first oil branch passage (N) leading to the first bearing and a second oil branch passage (R) leading to the second bearing, and the second oil supply passage is branched from the first oil branch passage. 【0249】 This configuration allows a portion of the lubricating oil flowing towards the first bearing to be diverted. In other words, it is easy to divert a portion of the lubricating oil and circulate it in the internal oil passages of the rotor as cooling oil to cool the rotor. 【0250】 This embodiment discloses a rotating electric machine system in which the oil discharge passage includes a first oil guide (184) that guides the lubricating oil supplied from the first oil branch passage to the first bearing to the oil circulation supply device, and a second oil guide (196) that guides the lubricating oil supplied from the second oil branch passage to the second bearing and the lubricating oil that has flowed through the rotor oil passage to the oil circulation supply device. 【0251】 This configuration allows the lubricating oil supplied to the first and second bearings, as well as the lubricating oil used to cool the rotor, to be easily recovered and then resupplied to the first bearings, the second bearings, and the internal oil passages of the rotor. 【0252】 This embodiment discloses a rotating electric machine system comprising a gas supply device (200) that supplies gas to the first bearing and the second bearing, the rotating electric machine housing having gas supply passages (1601-1603) that supply the gas supplied from the gas supply device to the first bearing and the second bearing, and a gas discharge passage (172) that discharges the gas from the first bearing and the second bearing, and an oil circulation supply device that recovers the gas that has flowed through the gas discharge passage and the lubricating oil that has flowed through the oil discharge passage, and resupplies the lubricating oil to the first oil supply passage. 【0253】 The gas supplied to the first and second bearings forms a gas curtain. This gas curtain seals the lubricating oil supplied to the first and second bearings. In other words, the lubricating oil supplied to the first and second bearings is blocked by the gas curtain. Therefore, the lubricating oil is prevented from splashing around the first or second bearing. This prevents, for example, the rotating shaft from becoming contaminated with lubricating oil. 【0254】 Furthermore, since the oil circulation supply system recovers both gas and lubricating oil together, there is no need to recover the gas and lubricating oil separately. Consequently, there is no need to install a gas recovery device in the rotating electric machine system. This avoids complicating the configuration of the rotating electric machine system. 【0255】 This embodiment discloses a rotating electric machine system in which the oil circulation supply device includes a gas-liquid separator (302) for separating the gas and the lubricating oil. 【0256】 Since the gas-liquid separator separates the gas and lubricating oil, even though the gas and lubricating oil are recovered together, only the lubricating oil can be resupplied to the first oil supply line. In other words, in this case, it is easy to circulate and supply lubricating oil to the first bearing, the second bearing, and the second oil supply line. 【0257】 This embodiment discloses a combined power system (500) comprising the above-described rotating electric machine system (10) and an internal combustion engine (200) having an output shaft (204) that rotates integrally with the rotating shaft. 【0258】 This makes it possible to construct a combined power system in which a rotating electric machine system and an internal combustion engine are integrated. In this case, despite the need to cool the rotor in the rotating electric machine system as described above, it is possible to avoid increasing the complexity or size of the rotating electric machine system. Therefore, it is possible to avoid increasing the complexity or size of the combined power system. Furthermore, it is also possible to avoid increasing the weight of the combined power system. 【0259】 Furthermore, the present invention is not limited to the disclosure described above, and can take various configurations without departing from the spirit of the invention. [Explanation of symbols] 【0260】 10... Rotating electrical machinery system 12... Rotating electrical machinery 14…Rotating electric machine housing 22…Storage room 24…Cooling jacket 26…First casing 28...Second casing 34...Rotor 36... Stator 40... Rotating shaft 42...Inner shaft 44...Outer shaft 58...Small cap nut 60...Large cap nut 62...Connecting hole 70...Cylindrical member 72…Permanent magnet 74…First bearing 80...First bearing holder 81...First outer stopper 82...First internal stopper 84...Second bearing 88...Second bearing holder 90...Second internal stopper 92...Second outer stopper 96...Flow straightening member 104...Inlet 106...Relay room 108…Through hole 110…Electromagnetic coil 112...Insulating substrate 132...Resolver 146...Battery 148...Thermistor 150...Current converter 152...Conversion circuit 154...Capacitor 156...Control circuit 161...Power module 162...Streaming channel 164…Upstream communication hole 166…Air relay path 172... Exhaust passage 174... Input passage 176…Main oilway 180…1st sub-oilway 181...Second auxiliary oil channel 184...First drain channel 188...Third sub oil path 192...Oil distributor 196...Second drain passage 200...Gas turbine engine 202…Engine housing 204…Output shaft 210... Leg section 214... Intake space 216...Extraction passage 217...Air vent 220... Shroud case 222... Compressor wheel 224... Turbine wheel 226... Diffuser 228... Combustor 230... Nozzle 234...Irrigation port 236...Chamber 274... Combustion air passage 275... Fuel supply nozzle 276…Relay port 302…Gas-liquid separator 304... Circulation supply line 308... Circulation pump 320... Compression pump 322... Flow port 324...Connecting hole 326...Plug 330...First section 332...Second section 334...Third section 336...Fourth section 340…Oil receiving recess 342…Inclined surface 350... Oil guide member 354... Oil passage inside rotor 356...First magnetic stopper 358...Second magnetic stopper 368... Downstream guide groove 370... Small diameter cylindrical section 372...Large diameter cylindrical section 382...Annular protrusion 384... Ring groove 385... Ring gap 386...First oil supply channel 388...Ring space 390…Upstream guide groove 392…Disc section 500... Combined power system 941... Third sub-junction 942...Fourth sub-junction 943...Exit road 1601...First hollow tube section 1602...Second hollow tube section 1603...Third hollow pipe section 3582...Second oil feed path L...1st air junction M...2nd air junction N...1st oil diversion channel R...2nd oil diversion channel

Claims

[Claim 1] A rotating electric machine system comprising a rotating electric machine having a rotor including a permanent magnet and a rotating shaft, and a rotating electric machine housing that rotatably supports the rotating shaft, A first bearing and a second bearing are interposed between the rotating electric machine housing and the rotating shaft, An oil circulation supply device that circulates and supplies lubricating oil to the first bearing and the second bearing, Equipped with, The rotating electric machine housing includes a first oil supply passage that supplies the lubricating oil supplied from the oil circulation supply device to the first bearing and the second bearing, It has a second oil supply passage that branches off from the first oil supply passage and supplies the lubricating oil toward the rotor, An internal rotor oil passage is formed inside the rotor, with the outer surface of the rotating shaft as its inner surface, and for circulating the lubricating oil that has flowed out from the second oil supply passage. The rotating electric machine housing has an oil discharge passage for discharging the lubricating oil that has flowed through the first oil supply passage, the second oil supply passage, and the rotor internal oil passage to the oil circulation supply device. The rotating electric machine system further includes an oil guide member provided on the outer surface of the rotating shaft, located outside the first bearing or the second bearing in the axial direction of the rotating shaft, which receives the lubricating oil from the second oil supply passage and guides the lubricating oil into the oil passage inside the rotor. The inlet of the oil passage inside the rotor is formed in an annular shape between the outer surface of the rotating shaft and the oil guide member in a rotating electric machine system. [Claim 2] A rotating electric machine system according to claim 1, wherein the rotor has a cylindrical member interposed between the rotating shaft and the permanent magnet in the diametrical direction of the rotating shaft, and at least a portion of the oil passage inside the rotor is formed between the outer surface of the rotating shaft and the inner circumferential wall of the cylindrical member. [Claim 3] A rotating electric machine system according to claim 1, wherein the oil passage in the rotor is a space that extends along the axial direction of the rotating shaft. [Claim 4] A rotating electric machine system according to claim 3, wherein the oil passage in the rotor extends at least from one end to the other end of the permanent magnet in the axial direction of the rotating shaft. [Claim 5] A rotating electric machine system according to claim 3, wherein the inlet of the rotor oil passage is located outward from the first bearing in the axial direction of the rotating shaft, and the outlet of the rotor oil passage is located inward from the second bearing in the axial direction of the rotating shaft. [Claim 6] A rotating electric machine system according to claim 1, wherein the first oil supply passage has a first oil branch passage leading to the first bearing and a second oil branch passage leading to the second bearing, and the second oil supply passage is a rotating electric machine system branched from the first oil branch passage. [Claim 7] In the rotating electric machine system according to claim 6, the oil discharge passage is A first oil conduit guides the lubricating oil supplied from the first oil branch to the first bearing to the oil circulation supply device, A rotating electric machine system having a second oil conduit that guides the lubricating oil supplied to the second bearing from the second oil branch passage and the lubricating oil that has flowed through the rotor's internal oil passage to the oil circulation supply device. [Claim 8] A rotating electric machine system according to any one of claims 1 to 7, comprising a gas supply device for supplying gas to the first bearing and the second bearing, The rotating electric machine housing has a gas supply passage for supplying the gas supplied from the gas supply device to the first bearing and the second bearing, and a gas discharge passage for discharging the gas from the first bearing and the second bearing. The oil circulation supply device is a rotating electric machine system that recovers the gas that has flowed through the gas discharge passage and the lubricating oil that has flowed through the oil discharge passage, and resupplies the lubricating oil to the first oil supply passage. [Claim 9] The rotating electric machine system according to claim 8, wherein the oil circulation supply device includes a gas-liquid separator for separating the gas and the lubricating oil. [Claim 10] A rotating electric machine system comprising a rotating electric machine having a rotor including a permanent magnet and a rotating shaft, and a rotating electric machine housing that rotatably supports the rotating shaft, A first bearing and a second bearing are interposed between the rotating electric machine housing and the rotating shaft, An oil circulation supply device that circulates and supplies lubricating oil to the first bearing and the second bearing, Equipped with, The rotating electric machine housing includes a first oil supply passage that supplies the lubricating oil supplied from the oil circulation supply device to the first bearing and the second bearing, It has a second oil supply passage that branches off from the first oil supply passage and supplies the lubricating oil toward the rotor, An internal rotor oil passage is formed inside the rotor to circulate the lubricating oil that has leaked out from the second oil supply passage. The rotating electric machine housing has an oil discharge passage for discharging the lubricating oil that has flowed through the first oil supply passage, the second oil supply passage, and the rotor internal oil passage to the oil circulation supply device. The rotating electric machine system further includes an oil guide member provided on the outer surface of the rotating shaft, which receives the lubricating oil from the second oil supply passage and guides the lubricating oil to the oil passage inside the rotor. The inlet of the rotor's internal oil passage is formed between the outer surface of the rotating shaft and the oil guide member. The system includes a gas supply device that supplies gas to the first bearing and the second bearing, The rotating electric machine housing has a gas supply passage for supplying the gas supplied from the gas supply device to the first bearing and the second bearing, and a gas discharge passage for discharging the gas from the first bearing and the second bearing. The oil circulation supply device recovers the gas that has flowed through the gas discharge passage and the lubricating oil that has flowed through the oil discharge passage, and resupplies the lubricating oil to the first oil supply passage. The aforementioned rotating electric machine housing has a cooling jacket inside the side wall, A portion of the aforementioned gas supply path is a rotating electric machine system located on the outer periphery side of the cooling jacket. [Claim 11] A rotating electric machine system according to claim 1 or 10, wherein the inlet of the oil passage in the rotor is located between the end of the rotating shaft and the permanent magnet in the axial direction of the rotating shaft. [Claim 12] A combined power system comprising a rotating electric machine system as described in claim 1 or 10, and an internal combustion engine having an output shaft that rotates integrally with the rotating shaft.

Images